CN104895667A - Variable-section exhaust gas bypass turbine for meeting demand of EGR (exhaust gas recirculation) recirculation - Google Patents

Abstract

The invention discloses a variable-section exhaust gas bypass turbine for meeting demand of EGR (exhaust gas recirculation) recirculation. The variable-section exhaust gas bypass turbine comprises a turbine shell and a power turbine; the turbine shell is provided with an internal air inlet flow way and an external air inlet flow way which are used for guiding the exhaust gas of an engine to the power turbine so as to drive the power turbine to rotate; the turbine shell is further provided with an exhaust gas bypass pipeline which can discharge exhaust gas without the power turbine, and an exhaust gas bypass valve for controlling the on-off of the exhaust gas bypass pipeline; when the gas inlet amount of the exhaust gas entering the turbine exceeds the pre-determined value, the exhaust gas bypass valve is opened so that a part of exhaust gas can be discharged through the exhaust gas bypass pipeline. When the engine is located under a high-speed working condition, the exhaust gas bypass valve can be opened so that a part of exhaust gas can be discharged through the exhaust gas bypass pipeline so as to avoid the excessive speed of a booster. The external air inlet flow way needs not to arrange to be a big area for avoiding the excessive speed of the booster under the high speed situation; when the adjusting valve is opened since the working condition of low speed and low load is turned to middle speed, the small area difference between internal and external flow ways can decrease the expansion loss.

Description

A kind of variable cross section exhaust gas bypass turbo machine meeting EGR circulation needs

Technical field

The present invention relates to technical field of engines, particularly a kind of variable cross section exhaust gas bypass turbo machine meeting RGR circulation needs.

Background technique

Along with the increasingly stringent of Abgasgesetz, EGR more and more applies on the engine, and EGR full name is Exhaust Gas Recirculation, and Chinese is translated into EGR, be that sub-fraction motor being produced waste gas sends cylinder participation burning again back to, effect is the discharge amount reducing NOx.

NOx is a kind of to the great gas of harm, mainly generates under high-temperature oxygen-enriched condition, combustion temperature and oxygen concentration higher, the endurance is longer, and the resultant of NOx is also more.In engine working process, if in good time, in appropriate amount portion is introduced in cylinder again, because the Main Ingredients and Appearance CO2 specific heat capacity in waste gas is larger, so the partial heat that burning produces can absorb and take cylinder out of by waste gas, and have certain diluting effect to air inlet, because this reducing maximum temperature and the oxygen content of engine combustion, thus decrease the generation of NOx compound.

On turbocharged and intercooled diesel engine, the major way realizing EGR be by turbine before waste gas introduce intercooler after, be called high pressure exhaust gas recirculation, in order to ensure the EGR rate of different operating mode, best mode adopts variable-area turbocharger, by the changes of section of pressurized machine regulate the front PT of turbine with in the pressure reduction of cold rear PK, drive EGR valve.

The maximum variable-area turbocharger of current employing increases swivel nozzle blade in turbine interior, changed the circulation passage of turbo machine, control more convenient by the aperture changing nozzle vane.But the waste gas due to motor discharge has the exhaust high temperature of 700 degrees centigrade, and there is the trend promoted further, the control system of exhaust high temperature to nozzle vane, driving mechanism, nozzle ring supporting disk and outside has strict requirement, and the moving element of impurity to complexity in the high-temp waste gas that motor is discharged causes reliability hidden danger.

And this series products, due to the price factor of costliness, is only used to high-end engine supercharging field, the type variable-area turbocharger limits marketing from cost and reliability two aspect.Except above-mentioned principal element, also there are some other technologies problems:

Problem 1, when the flow if reduced, need turn down nozzle vane aperture, and turbine inflow circumferential speed strengthens, and turbine becomes impulse wheel, and be unfavorable for making full use of of exhaust energy, turbine efficiency is on the low side, and causes engine exhaust back pressure too high.

Problem 2, during small leaf aperture, turbine inflow flow path increases, and strengthens along journey flow losses; Nozzle vane distance turbine is excessively far away, and air-flow losses by mixture is risen.

Problem 3, gap must be left in blade two ends, so that blade rotary, but this gap can cause air loss, reduces turbine efficiency.

Another uses more variable cross section application to be the double-layer channel variable-area turbocharger that Kang Yue science and technology is researched and developed, by the structural design to conventional turbine shell, adopt inside and outside double-deck gas-entered passageway combination, form different passage sections, effective segmentation utilizes the exhaust energy of motor, the all functions of variable-area turbine can be realized, and do not need to arrange complicated rotary vane type Pneumatic adjusting mechanism for adjusting, cost reduces greatly, reliability promotes greatly, will be following research direction.

The structural principle of this series products as shown in Figure 1, when motor operates in low speed, low-load, low pressure, close, 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, drives turbine acting by regulating valve 5.

As shown in Figure 2, when boost pressure acquires a certain degree, control final controlling element 7 and promote valve pin chip module 6, valve pin chip module 6 drives regulating valve 5 to open, air inlet inner flow passage 3 and air inlet outer flow passage 2 work simultaneously, air-flow flows into along inner flow passage flow direction 4 and outer flow passage flow direction 8, drives turbine acting.But this structure joining in examination and application process in reality, have also discovered a lot of problem.

As follows:

One, during high engine speeds, the exhausted air quantity of discharge is comparatively large, in order to ensure high speed performance, when avoiding high speed, turbine pressure is excessive and exceed the speed limit, double-layer channel area is comparatively large, but in the area distributions of double-layer channel, if inner flow passage area distributions is larger, then affect low-speed performance and the EGR rate of motor, if inner flow passage distributes less, inside and outside pipes' analysis product moment is very large, then when regulating valve 5 is opened, the expansion-loss of moment is excessive, and the middling speed of motor, middle load section are more difficult to control.

Two, in middling speed, the middle load section of motor, simple valve mechanism shown in Fig. 1,2 cannot accurate flow control and pressure, and the control deviation of flow, pressure not only can affect matching performance, more can affect the control of EGR rate, cause motor to discharge and exceed standard.

Three, the distribution of inside and outside runner can produce multiple whirlpools tongue, and gas flow is easy to influence each other, and causes turbine efficiency to reduce;

Four, the turbine structure being provided with inside and outside double flow channel is complicated, and turbo machine is again cast member, therefore conformity of production is difficult to control, and the casting deviation of double flow channel is large, larger on the matching performance impact of turbo machine.

Summary of the invention

For solving the problems of the technologies described above one, the invention provides a kind of variable cross section exhaust gas bypass turbo machine meeting RGR circulation needs, this turbo machine, under the prerequisite meeting EGR rate, can reduce again the expansion-loss of moment when regulating valve is opened.

The variable cross section exhaust gas bypass turbo machine meeting RGR circulation needs provided by the invention, comprise turbine case and power turbine, described turbine case is provided with water conservancy diversion engine exhaust to described power turbine and sentences the air inlet inner flow passage and air inlet outer flow passage that drive described power turbine to rotate

Described turbine case is also provided with without described power turbine and the exhaust gas bypass pipeline of combustion gas, and controls the exhaust gas bypass valve of described exhaust gas bypass pipeline break-make; When the air inflow that waste gas enters described turbo machine exceedes predetermined value, described exhaust gas bypass valve is opened to enable portion be discharged by described exhaust gas bypass pipeline.

Optionally, also comprise the regulating valve that aperture is adjustable, for regulating the air inflow of described air inlet outer flow passage; And,

Described regulating valve and described exhaust gas by-pass valve door linkage are configured to: when described regulating valve is opened into predetermined angle, and drive described exhaust gas bypass valve to open, now, air inflow reaches described predetermined value.

Optionally, described regulating valve is rotatable mid-valve, and during rotation, waste gas can enter through the both sides of valve body.

Optionally, described regulating valve and described exhaust gas bypass valve, the two one of have in regulating valve sense of rotation, the adjusting range of axial height change, another one has and contacts with described adjusting range the linkage portion coordinated, described exhaust gas bypass valve can be driven to move axially along described regulating valve and open when described regulating valve rotates.

Optionally, described regulating valve axially can contact along described regulating valve with described exhaust gas bypass valve; And also comprise drive portion, described drive portion comprises the end cap being installed on described turbine case, described in described end cap card lid, an end face of regulating valve rotates to drive described regulating valve;

Described end cap and described regulating valve, the two one of have in regulating valve sense of rotation, the adjusting range of axial height change, another one has and contacts with described adjusting range the linkage portion coordinated, described exhaust gas bypass valve can be driven to move axially along described regulating valve and open when described regulating valve rotates.

Optionally, the axial height of described adjusting range is around the center of rotation spiral of described regulating valve, and described linkage portion is contact with described adjusting range the adjustable lever coordinated.

Optionally, described adjusting range has along the mild protruding protuberance of described regulating valve sense of rotation, correspondingly in described adjusting range, forms recess; Described linkage portion is axial projection, and described axial projection is when described adjusting range is rotated, and described axial projection can slip over described recess, described protuberance successively.

Optionally, described regulating valve is provided with the cam thereupon rotated, and described exhaust gas bypass valve is provided with and can contacts with described cam edge the adjustable lever coordinated.

Optionally, also comprise spring, when the interlock power of described regulating valve and described exhaust gas bypass valve is cancelled, described spring controls described exhaust gas bypass valve and is reset to closed condition.

Optionally, also comprise valve base, it offers valve base inner flow passage interface, valve base outer flow passage interface, valve base exhaust gas bypass entrance, the outlet of valve base exhaust gas bypass; Described regulating valve and described exhaust gas bypass valve are all located at described valve base;

Described valve base is located between the inlet end of described outlet pipe and described turbine case.

Optionally, described exhaust gas bypass valve is directly installed on described turbine case, and described regulating valve is plugged in described turbine case, directly to regulate the air inflow entering described air inlet outer flow passage.

Optionally, described turbo machine is provided with air inlet outer flow passage, air inlet inner flow passage and exhaust gas bypass pipeline described in two groups corresponding to six cylinder engine, described regulating valve comprises two valve bodies connected, after plug-in mounting enters described turbine case, two described valve body difference, simultaneously correspondences control the air inflow of two described air inlet outer flow passages.

Optionally,

Also comprise and be located at described power turbine air inlet endface position and stator supporting disk in the form of a ring;

Described stator supporting disk is furnished with some first guide channels and the second guide channel along its circumferential interval, described first guide channel and described second guide channel have predetermined angle, the waste gas flowed out to enable described air inlet inner flow passage is guided to described power turbine through described first guide channel, and the waste gas that described air inlet outer flow passage flows out can be guided to described power turbine through described second guide channel.

Optionally, the anchor ring of described stator supporting disk is circumferentially with some stators being raised in described anchor ring, and described stator has the guiding gutter of through described stator, to form fluting stator;

Passage between adjacent described fluting stator forms described first guide channel, and described guiding gutter forms described second guide channel.

Optionally, the anchor ring of described stator supporting disk is provided with and is raised in described anchor ring and spaced long stator and short-range missile leaf, according to counterclockwise, passage between described long stator to described short-range missile leaf forms described second guide channel, and the passage between described short-range missile leaf to described long stator forms described first guide channel.

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

Turbo machine provided by the invention is provided with the exhaust gas bypass pipeline of the combustion gas without power turbine, now, also arranges the exhaust gas bypass valve controlling exhaust gas bypass pipeline break-make.Further, when the air inflow that waste gas enters described turbo machine exceedes predetermined value, open exhaust gas bypass valve and discharged by described exhaust gas bypass pipeline to enable portion.Therefore, when motor is in high-speed working condition, exhaust gas bypass valve can be opened, to enable portion discharge through exhaust gas bypass pipeline, avoid pressurized machine to exceed the speed limit.Then air inlet outer flow passage is without the need to being arranged to large size in order to avoid pressurized machine hypervelocity during high speed, can be arranged to compared with small size to ensure the turbine drives performance of middling speed, middle load and to circulate; And when going to middling speed operating mode by low speed, running on the lower load and open regulating valve, the comparatively small size official post of inside and outside runner obtains expansion-loss and is reduced.

The invention provides a kind of variable cross section exhaust gas bypass turbo machine meeting EGR circulation needs, comprise turbine case, air inlet inner flow passage and air inlet outer flow passage is provided with in described turbine case, air inlet inner flow passage and air inlet outer flow passage adopt non-all-round structure respectively, air inlet inner flow passage bears the air inlet of power turbine 0 ° ~ (150 ~ 230) °, and air inlet outer flow passage bears the air inlet of (150 ~ 230) ° ~ 360 °; Also be provided with exhaust gas bypass pipeline in described turbine case, this exhaust gas bypass pipeline and air inlet outer flow passage, air inlet inner flow passage be arranged in parallel, but without power turbine.

Below the further optimization of the present invention to such scheme:

This turbo machine also comprises power turbine, valve base, outlet pipe and control annex thereof, and described turbine case, valve base, outlet pipe are sealed connected together.

Further optimization: the regulating valve being provided with adjustable air inlet outer flow passage charge flow rate in described valve base.

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

Further optimization: the other end of regulating valve is provided with adjusting range, adjusting range is spiral-shaped structure, and its axial height helically rises around Pivot Point Center.

Further optimization:

The exhaust gas bypass valve of the action that can match with regulating valve is provided with in described exhaust gas bypass pipeline, exhaust gas by-pass valve door is arranged in valve base by exhaust gas by-pass valve axle sleeve, exhaust gas bypass valve and exhaust gas by-pass valve shaft room are provided with spring, and exhaust gas bypass valve is provided with the adjustable lever of the action that to match with adjusting range near the side of regulating valve.

During action, controlling annex drives regulating valve to rotate, while regulating air inlet outer flow passage air inflow, the adjusting range of regulating valve promotes adjustable lever, and exhaust gas bypass valve is opened, and Compress Spring, now, bypass exhaust is discharged, when regulating valve return from exhaust gas bypass pipeline, exhaust gas bypass valve is return under spring force effect, and waste gas is bypass no longer.

Further optimization: the position near power turbine in described turbine case is provided with stator supporting disk, stator supporting disk is provided with several fluting stators, and several fluting stators are evenly distributed ringwise.

Fluting stator neutral position is provided with guiding gutter, and the arrangement angle of fluting stator is 68 ° ~ 80 °, and two trough rims of guiding gutter carry out rotation acquisition by line of cut around the center of stator supporting disk, and the narrowest place of groove width presses 3mm and controls.

Described fluting stator adopts gas-solid combining nozzle form, during low engine speed low-load, turbo machine air inlet inner flow passage works, now the flow inlet angle of air inlet inner flow passage is obtained by formula tan (α)=2 π b/ (A/r), wherein b is turbine inlet width, be 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, and guarantee that two angles are basically identical, gas enters stator along air inlet inner flow passage, then enters power turbine along stator, and centre does not have corner loss, and pneumatic efficiency is high.

Along with engine speed promotes gradually, gas flow strengthens, air inlet outer flow passage can open participation air inlet along with regulating valve, outer flow passage flow inlet angle is also determined by the A/r of air inlet outer flow passage, guiding gutter angle designs by air inlet outer flow passage flow inlet angle, guarantee that two angles are basically identical, gas enters guiding gutter along air inlet outer flow passage, turbine is entered again along guiding gutter, avoid producing shock loss when installing complete stator (not having guiding gutter) and loss of turning round, not only increase efficiency, widen flow especially.And along with the quickening of airspeed, radial velocity component rises faster, and the existence of guiding gutter, makes the flow of high regime widen more obvious.

In real work, when motor is in low speed, low-load, regulating valve is closed, air inlet flows into turbine along outlet pipe, valve base gas access, valve base inner flow passage interface, turbine case inner flow passage entrance, air inlet inner flow passage, fluting stator, driving turbine does work, now, air-flow flows to turbine along two fluting stator zone lines, driving turbine does work, now only have air inlet inner flow passage to work, cross section is less, and also only enters along stator angular flux when flowing through stator, in air flow collection, pressure, lifting EGR rate before whirlpool can be improved.

When engine speed, load raise gradually, regulating valve starts to open, fraction flows through regulating valve, turbine is flowed into along valve base outer flow passage interface, turbine case outer flow passage entrance, air inlet outer flow passage, fluting stator, to adapt to the traffic demand increased gradually, in this process, by regulating the aperture of regulating valve, pressure before whirlpool can be adjusted, determine suitable EGR rate.

In the process regulating regulating valve, after regulating valve forwards several angle to, can by adjusting range to adjustable lever applied thrust, adjustable lever drives exhaust gas bypass valve Compress Spring, open waste gate passage, waste gas flows out along tail pipe exhaust Bypass outlet, valve base exhaust gas bypass entrance, the outlet of valve base exhaust gas bypass, the outlet of turbine case exhaust gas bypass entrance, turbine case exhaust gas bypass, and a part of exhaust energy of draining, when guaranteeing high engine speeds, high load, before pressurized machine whirlpool, pressure is unlikely excessive.And along with the increase of air inflow, air inlet can flow into along the guiding gutter on fluting stator, avoids the Airflow obstruction of high regime.

Another kind of optimized project: fluting stator comprises long stator and short-range missile leaf, and the length of long stator is greater than the length of short-range missile leaf, long stator and short-range missile interlobar septum are arranged.

The trailing edge of little stator and the leading edge of long stator keep at a certain distance away in a circumferential direction.Be convenient to air-flow from then on flow into when high engine speeds operating mode, can widen flow, reduce blocking, the function class of realization is similar to fluting stator.

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

The present invention adopts gas-solid combining nozzle, in conjunction with the advantage of flow-passage-changeable and swivel nozzle blade, solves the problems referred to above that they exist, and forms a variable cross section solution innovated.And, fluting stator in the present invention, length guide vane structure, compare the total length guide vane structure having application, flow inlet angle can be changed, widen high speed flow weight range, take into account the turbine performance of motor height low speed, use fixed stator, achieve the flow inlet angle adjustment that swivel nozzle blade could realize, turbine efficiency obviously promotes, and the existence of stator, decreases airflow reflux, not only increase turbine efficiency, more make air current flow smooth and easy, avoid the flow perturbation at aditus laryngis place, rate of fuel consumption realizes the significantly reduction on whole piece matched line.

Accompanying drawing explanation

Accompanying drawing 1 is the schematic diagram of double-layer channel variable-area turbocharger valve-closed state in background technique of the present invention;

Accompanying drawing 2 is schematic diagrams of double-layer channel variable-area turbocharger valve opening state in background technique of the present invention;

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

Accompanying drawing 4 is structural representations of turbo machine in the embodiment of the present invention 1, and this figure mainly illustrates turbine end air inlet endface position and internal motivation turbine;

Accompanying drawing 5 is the turbine case structural representations 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 representations in the embodiment of the present invention 1, and this illustrates and controls final controlling element and valve base installation cooperation;

Accompanying drawing 8 is valve base structural representations in the embodiment of the present invention 1;

Accompanying drawing 9 is that in the embodiment of the present invention 1, structural representation cut open by valve base;

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

Accompanying drawing 11 is that in the embodiment of the present invention 2, regulating valve and end cap are arranged schematic diagram;

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

Accompanying drawing 13 is regulating valve structural drawing in the embodiment of the present invention 2;

The schematic diagram that Figure 14 is is regulating valve in the embodiment of the present invention 2, end cap, exhaust gas bypass valve coordinate;

Accompanying drawing 15 is structural representations that in the embodiment of the present invention 3, exhaust gas bypass valve assembly coordinates with the regulating valve with cam type adjusting range;

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

Accompanying drawing 17 is that in the embodiment of the present invention 3, exhaust gas bypass valve assembly coordinates the regulating valve of screw type adjusting range and is installed on the schematic diagram of turbo machine;

Accompanying drawing 18 be in Figure 17 exhaust gas bypass valve assembly and regulating valve coordinate schematic diagram;

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

Accompanying drawing 20 is sectional drawings that in Figure 18, exhaust gas bypass valve assembly and regulating valve are plugged in turbine case;

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

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

Accompanying drawing 23 is the structural representations of stator of slotting in the embodiment of the present invention 1;

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

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

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

Accompanying drawing 27 is that efficiency comparative schemes, and wherein, A line is turbine efficiency line of the present invention, B line be do not improve before turbine efficiency line;

Accompanying drawing 28 be turbo machine and motor cooperation time oil consumption correlation curve figure;

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

Accompanying drawing 30 is efficiency comparison plotted curves of long and short stator turbo machine and slot stator turbo machine, existing general exhaust gas bypass turbo machine.

In figure: 1-turbine case; 2-air inlet outer flow passage; 3-air inlet inner flow passage; 4-inner flow passage flow direction; 5-regulating valve; 6-valve pin chip module; 7-controls final controlling element; 8-outer flow passage flow direction; 9-turbine case exhaust gas bypass entrance; 10-turbine case outer flow passage entrance; 11-turbine case inner flow passage entrance; 12-slots stator; 13-turbine case exhaust gas bypass exports; 14-outlet pipe; 15-valve base; 16-tail pipe exhaust Bypass outlet; 17-outlet pipe gas outlet; 18-valve base inner flow passage interface; 19-valve base outer flow passage interface; 20-valve base exhaust gas bypass exports; 21-exhaust gas by-pass valve axle sleeve; 22-regulating valve axle sleeve; 23-valve base gas access; 24-valve base exhaust gas bypass entrance; 25-adjusting range; 26-exhaust gas bypass valve; 27-spring; 28-adjustable lever; 29-guiding gutter; 30-stator supporting disk; 31-power turbine; The long stator of 32-; 33-short-range missile leaf; 34-trailing edge; 35-leading edge; 36-line of cut; 37-bypath valve assembly; 38-upper shell; 39-upper-lower casing sealing gasket; 40-bypath valve assembly sealing gasket; 41-lower shell body; 41a-assembly exhaust gas bypass exports; 42-bypath valve supporting axle; 43-guide sleeve; 44, bolt; 45-screw; 46, end cap; 47-coordinates adjusting range; 47a-axial projection; 48-exhaust gas bypass Valve controlling final controlling element.

Embodiment

In order to make those skilled in the art understand technological scheme of the present invention better, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.

Embodiment 1, and as shown in Fig. 3,4,5, a kind of variable cross section exhaust gas bypass turbo machine meeting EGR circulation needs, comprise turbine case 1, power turbine 31, valve base 15, outlet pipe 14 and control annex, valve base 15 is located between outlet pipe 14 and turbine case 1.In order to ensure effective work, described turbine case 1, valve base 15, outlet pipe 14 are sealed connected together.

Be provided with air inlet inner flow passage 3 and air inlet outer flow passage 2 in described turbine case 1, the waste gas that engine exhaust pipe 14 is discharged can enter air inlet inner flow passage 3 and air inlet outer flow passage 2.In the present embodiment, air inlet inner flow passage 3 and air inlet outer flow passage 2 adopt non-all-round structure respectively, as shown in Figure 5, air inlet inner flow passage 3 bears the air inlet of power turbine 0 ° ~ (150 ~ 230) °, and air inlet outer flow passage 2 bears the air inlet of (150 ~ 230) ° ~ 360 °.Simulation analysis and practice show, the distribution of this kind of angle is arranged, the efficiency optimization under each operating mode.

The end face area (i.e. the air inlet end face of turbine case 1) that described turbine case 1 is connected with valve base 15 is provided with the turbine case outer flow passage entrance 10, the turbine case inner flow passage entrance 11 that are communicated with air inlet inner flow passage 3 with air inlet outer flow passage 2 respectively, the waste gas that outlet pipe 14 is discharged 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, rotate to drive power turbine 31, thus drive the gas compressor end action of turbosupercharger, to implement air intake pressurized.

Also be provided with exhaust gas bypass pipeline in described turbine case 1, this exhaust gas bypass pipeline and air inlet outer flow passage 2, air inlet inner flow passage 3 are set up in parallel, but without power turbine 31.Namely portion can flow to exhaust gas bypass pipeline, but can be expelled to outside, and does not play a part to drive power turbine 31 to rotate.

Now, the end face area that described turbine case 1 is connected with valve base 15 is also provided with the turbine case exhaust gas bypass entrance 9 with exhaust gas bypass pipeline connection, and the exhaust end inner hole wall of described turbine case 1 is provided with and exports 13 with the turbine case exhaust gas bypass of exhaust gas bypass pipeline connection.

Valve base 15 is provided with valve base inner flow passage interface 18, valve base outer flow passage interface 19, valve base exhaust gas bypass outlet 20, is communicated with respectively with turbine case inner flow passage entrance 11, turbine case outer flow passage entrance 10, turbine case exhaust gas bypass entrance 9; Valve base 15 is also provided with valve base gas access 23 and valve base exhaust gas bypass entrance 24.In Fig. 7,8, valve base 15 top is located in valve base inner flow passage interface 18, valve base outer flow passage interface 19, valve base exhaust gas bypass outlet 20, and valve base gas access 23 and valve base exhaust gas bypass entrance 24 are located at bottom.

Correspondingly, as shown in Figure 6, described outlet pipe 14 is provided with the outlet pipe gas outlet 17 be communicated with turbine case inner flow passage entrance 11 by valve base 15 and turbine case outer flow passage entrance 10 and the tail pipe exhaust Bypass outlet 16 be communicated with turbine case exhaust gas bypass entrance 9 by valve base 15.

Outlet pipe 14 discharge waste gas a part is flowed out by outlet pipe gas outlet 17, by valve base 15 flow into distribute in turbine case outer flow passage entrance 10 and turbine case inner flow passage entrance 11 after enter power turbine 31 again.

Another part bypass exhaust flows out from tail pipe exhaust Bypass outlet 16, is flowed into the turbine case exhaust gas bypass entrance 9 linked together by valve base 15, flows out from turbine case exhaust gas bypass outlet 13, without power turbine 31, directly discharges turbine case 1.

As shown in Fig. 7,8,9,10, described valve base 15 is provided with valve base inner flow passage interface 18, valve base outer flow passage interface 19 and valve base exhaust gas bypass outlet 20, the two ends of valve base inner flow passage interface 18 are communicated with outlet pipe gas outlet 17 with turbine case inner flow passage entrance 11 respectively, and the two ends of valve base outer flow passage interface 19 are communicated with outlet pipe gas outlet 17 with turbine case outer flow passage entrance 10 respectively;

Valve base exhaust gas bypass outlet 20 is communicated with tail pipe exhaust Bypass outlet 16 with turbine case exhaust gas bypass entrance 9 respectively with valve base exhaust gas bypass entrance 24.

In the present embodiment, be also provided with in described valve base 15 adjustable air inlet outer flow passage 2 charge flow rate regulating valve 5;

Particularly, regulating valve 5 is arranged in valve base 15 by regulating valve axle sleeve 22, and wherein one end of regulating valve 5 is connected with valve pin chip module 6, is connected with control accessory drive by valve pin chip module 6.

Control annex and comprise the control final controlling element 7 be connected with valve pin chip module 6; Control final controlling element 7 and valve pin chip module 6 are arranged on the outside of turbine case 1.

This regulating valve 5 preferably adopts rotatable mid-valve, and as shown in Figure 10, regulating valve 5 can rotate around its central axis.In Fig. 9, passage between valve base outer flow passage interface 19 and valve base gas access 23 is all blocked by the door body of regulating valve 5, when regulating valve 5 rotates under the driving of valve pin chip module 6, the inwall of its both sides and above-mentioned passage forms opening, then allow waste gas to pass through.

Compared to the bleed valve door shown in background technique, this kind of mid-valve mechanism, when rotarily opening, proportional between its aperture and angle of swing, air inflow and suction pressure can realize accurate control, thus realize the matched well with motor, and improve the accurate control to EGR rate, make motor meet emission standard.

The turbo machine provided in above-described embodiment is provided with without power turbine 31 and the exhaust gas bypass pipeline of combustion gas, now, also arranges the exhaust gas bypass valve 26 controlling exhaust gas bypass pipeline break-make.Further, when the air inflow that waste gas enters described turbo machine exceedes predetermined value, open exhaust gas bypass valve and discharged by described exhaust gas bypass pipeline to enable portion.Therefore, when motor is in high-speed working condition, exhaust gas bypass valve 26 can be opened, to enable portion discharge through exhaust gas bypass pipeline, avoid pressurized machine to exceed the speed limit.Then air inlet outer flow passage 2 is without the need to being arranged to large size in order to avoid pressurized machine hypervelocity during high speed, can be arranged to circulate with the turbine drives performance and EGR that ensure middling speed, middle load compared with small size; And when going to middling speed operating mode by low speed, running on the lower load and open regulating valve 5, the comparatively small size official post of inside and outside runner obtains expansion-loss and is reduced.

Further, exhaust gas bypass valve 26 and regulating valve 25 can link and be configured to: when regulating valve 5 is opened into predetermined angle, and drive described exhaust gas bypass valve 26 to open, now, air inflow reaches described predetermined value.

Concrete linked manner can be as follows:

As shown in Figure 9, one end of regulating valve 5 is installed on valve base 15 by regulating valve axle sleeve 22, and the other end of regulating valve 5 is provided with adjusting range 25, and adjusting range 25 is spiral-shaped structure, and its axial height helically rises around Pivot Point Center.

The exhaust gas bypass valve 26 of the action that can match with regulating valve 5 is provided with in described exhaust gas bypass pipeline, exhaust gas bypass valve 26 is arranged in valve base 15 by exhaust gas by-pass valve axle sleeve 21, be provided with spring 27 between exhaust gas bypass valve 26 and exhaust gas by-pass valve axle sleeve 21, exhaust gas bypass valve 26 is provided with the adjustable lever 28 of the action that to match with adjusting range 25 near one end of regulating valve 5.As shown in Figure 9, exhaust gas bypass valve 26 and regulating valve 5 axis being parallel ground are arranged, and adjustable lever 28 towards adjusting range 25, and contacts cooperation with it.

During action, described control final controlling element 7 promotes valve pin chip module 6, valve pin chip module 6 drives regulating valve 5 to rotate, while regulating air inlet outer flow passage 2 air inflow, when angle of swing reaches certain value, adjustable lever 28 can move along the Hand of spiral of adjusting range 25, then the adjusting range 25 of regulating valve 5 can promote adjustable lever 28 and moves axially, exhaust gas bypass valve 26 is opened, and Compress Spring 27, now, bypass exhaust flows into from valve base exhaust gas bypass entrance 24, turbine case exhaust gas bypass entrance 9 is flow to from valve base exhaust gas bypass outlet 20, and flow out from turbine case exhaust gas bypass outlet 13, when regulating valve 5 return, exhaust gas bypass valve 26 is return under the effect of spring 27 elastic force, waste gas is bypass no longer.

One embodiment 2 is also provided below, substantially the same manner as Example 1, but have employed different linked manner, regulating valve 5 structure also changes (will mention later) slightly, please continue to refer to Figure 11-14.

In this embodiment, one end that regulating valve 5 is connected with valve pin chip module 6 is provided with the adjusting range 25 that axial height changes.Now, also comprise the end cap 46 coordinated with regulating valve 5 end Ka Gai, end cap 46 can be fixed on the housing of turbine case 1, and end cap 46 is provided with the structure that adjusting range 25 corresponding thereto coordinates, valve pin chip module 6 is positioned at outside end cap 46, and regulating valve 5 can be driven to rotate.

Particularly, in this embodiment, end cap 46 is provided with the cooperation adjusting range 47 coordinated with adjusting range 25, coordinates adjusting range 47 to have axial projection 47a; Adjusting range 25 is provided with the recess arranged along described sense of rotation, correspondingly forms protuberance, and recess relatively gently transits to protuberance.As shown in Figure 11,14, when valve pin chip module 6 rotating drive regulating valve 5 rotates, adjusting range 25 relative engagement adjusting range 46 is rotated, when axial projection 47a slips over recess and contacts protuberance, be rotated further, then axial projection 47a jack-up adjusting range 25 lentamente, regulating valve 5 correspondingly moves vertically.

Therefore be designed to regulating valve 5 and exhaust gas bypass valve 26 and axially can contact along regulating valve, then when regulating valve 5 moves axially under coordinating adjusting range 46 to drive, also drive exhaust gas bypass valve 26 moves axially, to open exhaust gas bypass valve 26 simultaneously.

Interlock set-up mode in above-mentioned two embodiments, all the adjusting ranges 25 forming an axial height change on parts, the linkage portion (such as adjustable lever 28, coordinate the axial projection of adjusting range 47) contacted with its coupling is set in another parts again, thus be straight line motion by convert rotational motion, realize coordinated signals.Known, in above-described embodiment, adjusting range 25 and the linkage portion set-up mode mated with it are not limited to above-mentioned two kinds, such as, adjusting range 25 can be located at exhaust gas bypass valve 26, and regulating valve 5 is located at by adjustable lever 28, certainly, adjustable lever 28 is located at exhaust gas bypass valve 26 adjusting range 25 can be avoided to interfere waste gas to circulate; Adjusting range 25 can be located at end cap, and coordinates adjusting range 46 to be located at regulating valve 5.

The engaging coupling of above-mentioned end cap and regulating valve 5 is arranged, and also makes the stability of whole linking mechanism better.Accordingly, as shown in Figure 12,13, axial projection, recess are all set to two, and are symmetrical arranged along the center line of corresponding component end face, then, after coordinating, stability is higher, not easily offsets.

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

Regulating valve 5 one end connection valve door bolt chip module 6, the other end is provided with the adjusting range 25 of cammingly, and exhaust gas bypass valve 26 is provided with and can contacts the adjustable lever 28 coordinated with cam edge.Then when regulating valve 5 rotates, adjustable lever 8 moves axially along exhaust gas bypass valve 26, thus opens valve.Herein, the adjusting range 25 of cammingly should be designed to, and when turning to predetermined angle, adjustable lever 28 just contacts with cam edge and backed down movement, just opens exhaust gas bypass valve 26 to meet when aforesaid air inflow acquires a certain degree.

In above-described embodiment, exhaust gas bypass valve 26 and regulating valve 5 realize coordinated signals, then only need arrange the drive portion of regulating valve 5, without the need to separately establishing the parts controlling exhaust gas bypass valve 26, and compact structure, simply; And exhaust gas bypass valve 26 is changed by the aperture of regulating valve 5 and controls, then the keying of exhaust gas bypass valve 25 controls realistic air inflow to change, and compares to control separately, and it is more accurate obviously to control.

It should be noted that, in above-described embodiment, valve base 15 is set to install the parts such as regulating valve 5, exhaust gas bypass valve 26, thus is convenient to the installation of each parts, and realize turbine case 1 and be communicated with the controlled of outlet pipe 14.The present invention also provides alternative valve set-up mode, and structure is compacter, as shown in figs. 15 to 20.

In this embodiment, be provided with exhaust gas bypass valve assembly 37, be provided separately with regulating valve 5, exhaust gas bypass valve 37 assembly is directly installed on turbine case 1, and regulating valve 5 is directly installed in turbine case 1, as shown in figure 20, the door body of regulating valve 5 directly inserts in 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, forms opening with conducting waste gas.In figure, regulating valve 5 runs through the air inlet mounting end of turbine case 1, and one end connects exhaust gas bypass valve assembly 37, and the other end connects the valve pin chip module 6 driving it to rotate.

Now, the air inlet of turbine case 1 is installed end face and then can be directly communicated with outlet pipe 14, correspondingly, outlet pipe 14 correspondingly set out respectively with air inlet inner flow passage 3, relief opening that air inlet outer flow passage 2 is corresponding.

Because linked manner is different, the installation requirement of valve is also different.Figure 16,17 can be compared understand, the adjusting range 25 of screw type, the adjusting range 25 of axial projection type, exhaust gas bypass valve 26 and regulating valve 5 parallel to an axis ground are arranged, and when being set to the adjusting range 25 of cam type, then exhaust gas bypass valve 26 and regulating valve 5 are by setting at an angle, Figure 15,16, the two is almost vertically arranged.

As shown in Figure 18,19, this bypath valve assembly 37 specifically comprises exhaust gas bypass valve 26, upper shell 38, lower shell body 41, and upper shell 38 is connected with lower shell body 41 and forms valve pocket, and lower shell body 41 sidewall offers assembly exhaust gas bypass outlet 41a.Exhaust gas bypass valve 26 can by bypath valve supporting axle 42 support and connection, and bypath valve back shaft 42 is placed in valve pocket, and is provided with spring 27 with the end of upper shell 38, to provide reposition force.The end of lower shell body 41 is provided with valve port, and when exhaust gas bypass valve 26 is opened, waste gas enters assembly exhaust gas bypass outlet 41a through valve port.

In Figure 19, the end face of exhaust gas bypass valve 26 is outstanding forms adjustable lever 28, and namely adjustable lever 28 is integrally formed at exhaust gas bypass valve 26, and be convenient to processing, coordinated signals is also more reliable.

In the valve pocket of exhaust gas bypass valve assembly 37, guide sleeve 43 can also be set, bypath valve supporting axle 42 runs through this guide sleeve 43, and when exhaust gas bypass valve 26 moves axially, bypath valve supporting axle 42 slides along guide sleeve 43, in order to avoid exhaust gas bypass valve 26 skew moves axially, affect exhaust gas bypass.In Figure 19, bypath valve supporting axle 42 has bigger diameter end, with supported spring 27.

The turbo machine that above embodiment provides is not only applicable to four cylinder engine, can also be applicable to six cylinder engine.Namely the structure of Fig. 4-10 corresponds to four cylinders, need during six cylinders to arrange two groups of air inlet inner flow passages 3, air inlet outer flow passage 2, exhaust gas bypass pipeline, as shown in Figure 16,17, the air inlet of turbine case 1 is installed end face and is correspondingly provided with two turbine case exhaust gas bypass entrances 9, turbine case outer flow passage entrance 10, turbine case inner flow passage entrance 11.Now, two groups of above-mentioned valves can be set.

Also provide a kind of for six cylinder engine herein, structure is more compact, volume is little, and control more simply, valve mechanism accurately.

As shown in Figure 13,18,20, regulating valve 5 comprises two valve bodies connected, after plug-in mounting enters turbine case 1, and two valve bodies corresponding air inflow controlling two outer flow passages 2 respectively.This regulating valve 5 still links with an exhaust gas bypass valve 26 and installs, and namely on original regulating valve 5, adds a valve door body, is namely applicable to six cylinder engine, be equivalent to the air inflow of a Valve controlling two runners, be easy to realize accurate control.

Provide the mode of multiple regulating valve 5 and exhaust gas bypass valve 26 interlock in above-described embodiment, be appreciated that it is also feasible for controlling exhaust gas bypass valve 26 separately, the embodiment 4 as shown in Figure 21,22.Similar with the air inlet outer flow passage bleed valve mentioned in background technique, also can be equipped with corresponding exhaust gas bypass Valve controlling final controlling element 48 for exhaust gas by-pass valve door 26, then according to corresponding air inlet signal, the keying of exhaust gas bypass valve 26 can be controlled.Exhaust gas bypass Valve controlling final controlling element 48 is identical with the working principle controlling final controlling element 7, as shown in figure 22, the rod end of exhaust gas bypass Valve controlling final controlling element 48 can extend under pneumatic pressure, and pin chip module rotates, and then drive exhaust gas bypass valve 26 to rotate, to close or to open valve port.

It should be noted that, in above-described embodiment, when regulating valve 5 and exhaust gas bypass valve 26 link, when interlock power is cancelled, by arranging spring 27, making exhaust gas bypass valve 26 to be reset to original state.The linked manner that spring 27 coordinates in conjunction with above-mentioned multiple adjusting range 25, simply, reliably achieves the unlatching of exhaust gas bypass valve 26.Be appreciated that when being controlled exhaust gas bypass valve 26 by exhaust gas bypass Valve controlling final controlling element 48 and opening and closing, then without the need to arranging resetting means.In fact, except the exhaust gas bypass valve 26 mentioned links scheme, also have other schemes can realize the interlock of exhaust gas bypass valve 26 and regulating valve 5, and without the need to arranging return structure.Such as, the end of regulating valve 5 is provided with gear, and exhaust gas bypass valve 26 is provided with tooth bar, or regulating 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 and easy, also not easily interferes valve port.

The present invention is also to driving the intake method of power turbine 31 to do improvement.

As shown in Fig. 4,23, non-blade nozzle is provided with near the position of power power turbine 31 in described turbine case 1, the waste gas that air inlet inner flow passage 3 and air inlet outer flow passage 2 are discharged to be imported to the blade of power turbine 31, the present embodiment is provided with fluting stator 12 in the position near non-blade nozzle, near the position of power turbine 31, stator supporting disk 30 is installed in described turbine case 1, stator supporting disk 30 is provided with several fluting stators 12, for realizing air inlet more equably, several fluting stators 12 are evenly distributed ringwise.

The neutral position of fluting stator 12 is provided with guiding gutter 29.Namely some stators being raised in anchor ring are set in the anchor ring circumference of stator supporting disk 30, then offer the guiding gutter 29 running through stator, then form fluting stator.The arrangement angle B of fluting stator 12 (as shown in figure 23, this angle is that the tangent line of fluting stator 12 medial axis, fluting stator 12 are near the tip at stator supporting disk 30 center and stator supporting disk 30 line of centres, the angle of the two) can be 68 ° ~ 80 °, two trough rims of guiding gutter 29 can carry out rotation by line of cut 36 (fluting stator 12 is near the tip at stator supporting disk 30 center and stator supporting disk 30 center line line) around the center of stator supporting disk 30 and obtain, and 3mm control is pressed at the narrowest place of groove width.

Described fluting stator 12 adopts gas-solid combining nozzle form, namely the function of gas flow and solid nozzle is combined, during low engine speed low-load, turbo machine air inlet inner flow passage 3 works, those skilled in the art are known, now air inlet inner flow passage 3 flow inlet angle is obtained by formula tan (α)=2 π b/ (A/r), wherein b is turbine inlet width, it is definite value, flow inlet angle is then determined by the A/r of air inlet inner flow passage 3, wherein, A is turbine case 1 zero sectional area, R is the distance of zero cross section barycenter to turbine case 1 axle center, as shown in figure 24, Figure 24 is turbine case A, r schematic diagram.

Stator angle (angles between two fluting stators 12) is designed by air inlet inner flow passage 3 flow inlet angle, guarantee that two angles are basically identical, then gas enters fluting stator 12 along air inlet inner flow passage 3, power turbine 31 is entered again along fluting stator 12, centre does not have corner loss, and pneumatic efficiency is high.

Along with engine speed promotes gradually, gas flow strengthens, air inlet outer flow passage 2 can open participation air inlet along with regulating valve 5, air inlet outer flow passage 2 flow inlet angle is also determined by the A/r of air inlet outer flow passage 2, guiding gutter 29 angle designs by air inlet outer flow passage 2 flow inlet angle, guarantee that two angles are basically identical, gas enters guiding gutter 29 along air inlet outer flow passage 2, power turbine 31 is entered again along guiding gutter 29, avoid producing shock loss when installing complete stator (not having guiding gutter 29) and loss of turning round, not only increase efficiency, widen flow especially.And along with the quickening of airspeed, air-flow radial velocity component rises faster, and the existence of guiding gutter 29, makes the flow of high regime widen more obvious.

With gas flow schematic diagram in Figure 23, when low engine speed low-load, air-flow is only along N to (angle is α, i.e. flow inlet angle) enter power turbine 31, when engine speed promotes gradually, air-flow can merge into H and work to power turbine 31 along M (angle is β, i.e. flow inlet angle), N both direction, and in figure, δ is the airflow direction excursion flowing into power turbine 31.

This embodiment sentencing when arranging valve base 15 is that example illustrates exhaust flow path.

In real work, when motor is in low speed, low-load, regulating valve 5 is closed, air inlet flows into power turbine 31 along the passage between outlet pipe 14, valve base gas access 23, valve base inner flow passage interface 18, turbine case inner flow passage entrance 11, air inlet inner flow passage 3, adjacent notch stator 12, drives power turbine 31 to do work.

Now, air-flow flows to power turbine 31 along two fluting stator 12 zone lines, power turbine 31 is driven to do work, air inlet inner flow passage 3 is only had to work, cross section is less, and also only enters along stator angular flux when flowing through fluting stator 12, namely in Figure 20 N to, in air flow collection, pressure, lifting EGR rate before whirlpool can be improved.

When engine speed, load raise gradually, regulating valve 5 starts to open, fraction flows through regulating valve 5, power turbine 31 is flowed into along valve base outer flow passage interface 19, turbine case outer flow passage entrance 10, air inlet outer flow passage 2, fluting stator 12, to adapt to the traffic demand increased gradually, in this process, by regulating the aperture of regulating valve 5, pressure before whirlpool can be adjusted, determine suitable EGR rate.

In the process regulating regulating valve 5, (usually high engine speeds section is corresponded to) after regulating valve 5 forwards several angle to, adjustable lever 28 applied thrust can be given by adjusting range 25, adjustable lever 28 drives exhaust gas bypass valve 26 Compress Spring 27, open exhaust gas bypass pipeline, waste gas is along tail pipe exhaust Bypass outlet 16, valve base exhaust gas bypass entrance 24, valve base exhaust gas bypass outlet 20, turbine case exhaust gas bypass entrance 9, turbine case exhaust gas bypass outlet 13 is flowed out, to drain a part of exhaust energy, guarantee high engine speeds, during high load, before pressurized machine whirlpool, pressure is unlikely excessive.

And along with the increase of air inflow, air inlet can flow into along the guiding gutter 29 on fluting stator 12, namely in Figure 23 M to, M to, N to while air inlet, avoid the Airflow obstruction of high regime.

As shown in Figure 25,26, the existence of stator, decreases airflow reflux, not only increases turbine efficiency, more makes air current flow smooth and easy, avoids the flow perturbation at aditus laryngis place, ensures turbine efficiency.

In addition, pressure ratio, the flow of turbo machine are larger to its performance impact, and be passage section to its decisive action of flow, prior art relies on the runner design of turbine case 1 to control passage section, but as stated in the Background Art, the conformity of production of cast turbine engine is difficult to control, and correspondingly flow is difficult to control.Be provided with guide vane structure in the present embodiment, then can by wicket gate control flow area, and guide vane structure can precision machining be formed, flow area can obtain precise hard_drawn tuhes, thus not by the impact of the machining accuracy of turbine case 1 own.

After stator is set, make turbo machine, motor obtains obvious performance boost, as follows:

1, turbine efficiency obviously promotes, and as shown in figure 27, the thicker black line A in top is efficiency line of the present invention to efficiency comparative figure, the thinner black line B in below be do not improve before turbine efficiency line.

2, with motor cooperation oil consumption correlation curve as shown in figure 28, adopt turbosupercharger of the present invention, rate of fuel consumption realizes the significantly reduction on whole piece matched line.

Embodiment 5, and on above-described embodiment basis, the present invention also provides another kind of stator to arrange form, and as shown in figure 29, stator comprises long stator 32 and short-range missile leaf 33, and the length of long stator 32 is greater than the length of short-range missile leaf 33, and long stator 32 and short-range missile leaf 33 interval are arranged.

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 will have a segment distance in a circumferential direction with the leading edge 35 of long stator 32, be convenient to air-flow from then on flow into when high engine speeds operating mode, can widen flow, reduce blocking, the function class of realization is similar to the fluting stator 12 of previous embodiment.Namely long stator 32 according to several angle along stator supporting disk 30 circumferential array, short-range missile leaf 33 is according to another angular array, then according to counterclockwise, passage between long stator 32 and short-range missile leaf 33 forms the water conservancy diversion runner with air inlet inner flow passage 3 conducting, and the passage between short-range missile leaf 33 and long stator 32 forms the water conservancy diversion runner with air inlet outer flow passage 2 conducting.Specific works process can refer to above-mentioned fluting stator 12 and understands.

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

Wherein, arrangement angle B is, the tangent line of long stator 32 medial axis, the tip of long stator 32 near stator supporting disk 30 center and the line of centres of stator supporting disk 30, the angle of the two; Arrangement angle A is, the tangent line of short-range missile leaf 31 medial axis, the tip of short-range missile leaf 31 near stator supporting disk 30 center and the line of centres of stator supporting disk 30, the angle of the two.

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

The black C line that the thinnest black line A in top is length stator turbine efficiency line, below is the thickest is general exhaust gas bypass turbine efficiency line, middle black line B is fluting stator turbine efficiency line.Can be found out by upper table, long stator 32 is set, the turbine efficiency of short-range missile leaf 33 is even higher than fluting stator 12 structure.

Can find out from the above description, no matter be fluting stator 12, or being equipped with of long stator 32, short-range missile leaf 33, all to form the first guide channel, (i.e. the two not parallel setting of the second guide channel that two kinds have predetermined angle, this angle 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 guided to described power turbine 31 through the first guide channel, the waste gas that air inlet outer flow passage 2 flows out can be guided to described power turbine 31 through described second guide channel.As above, then the passage between adjacent notch stator 12 forms described first guide channel, and guiding gutter 29 forms the second guide channel; According to counterclockwise, the passage between long stator 32 to short-range missile leaf 33 forms the second guide channel, and the passage between short-range missile leaf 33 to long stator 32 forms the first guide channel.

As long as the waste gas of air inlet inner flow passage 3 and air inlet outer flow passage 2 can be guided into power turbine 31 respectively, widen range of flow, namely technique effect as above can be produced, obviously, 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, be easy to processing, and do not hinder air-flow, water conservancy diversion effect is best.In addition, water conservancy diversion supporting disk 30 and turbine case 31 set up separately, and water conservancy diversion supporting disk 30 can take fine finishing, and precision is easy to ensure, thus ensures the distribution of air-flow further, guarantees turbine efficiency.

We have been described in detail invention according to national patent method now, can identify improvement or the replacement of specific embodiment disclosed herein for those skilled in the art.These amendments are within the spirit and scope of the present invention.

Claims (22)

1. one kind meets the variable cross section exhaust gas bypass turbo machine of RGR circulation needs, comprise turbine case (1) and power turbine (31), described turbine case (1) is provided with water conservancy diversion engine exhaust to described power turbine (31) and sentences the air inlet inner flow passage (3) and air inlet outer flow passage (2) that drive described power turbine (31) to rotate, it is characterized in that

Described turbine case (1) is also provided with the exhaust gas bypass pipeline of combustion gas without described power turbine (31), and controls the exhaust gas bypass valve (26) of described exhaust gas bypass pipeline break-make; When the air inflow that waste gas enters described turbo machine exceedes predetermined value, described exhaust gas bypass valve (26) is opened to enable portion be discharged by described exhaust gas bypass pipeline.

2. variable cross section exhaust gas bypass turbo machine as claimed in claim 1, is characterized in that, also comprise the adjustable regulating valve of aperture (5), for regulating the air inflow of described air inlet outer flow passage (2); And,

Described regulating valve (5) and described exhaust gas bypass valve (26) are linked and are configured to: when described regulating valve (5) is opened into predetermined angle, described exhaust gas bypass valve (5) is driven to open, now, air inflow reaches described predetermined value.

3. variable cross section exhaust gas bypass turbo machine as claimed in claim 2, it is characterized in that, described regulating valve (5) is rotatable mid-valve, and during rotation, waste gas can enter through the both sides of valve body.

4. variable cross section exhaust gas bypass turbo machine as claimed in claim 3, it is characterized in that, described regulating valve (5) and described exhaust gas bypass valve (26), the two one of have in regulating valve (26) sense of rotation, the adjusting range (25) of axial height change, another one has and contacts with described adjusting range (25) linkage portion coordinated, described exhaust gas bypass valve (26) can be driven to move axially along described regulating valve (5) and open when described regulating valve (5) rotates.

5. variable cross section exhaust gas bypass turbo machine as claimed in claim 3, is characterized in that, described regulating valve (5) axially can contact along described regulating valve (5) with described exhaust gas bypass valve (26); And, also comprise drive portion, described drive portion comprises the end cap (46) being installed on described turbine case (1), and an end face of described end cap (46) the card described regulating valve of lid (5) rotates to drive described regulating valve (5);

Described end cap (46) and described regulating valve (5), the two one of have in regulating valve (5) sense of rotation, the adjusting range (25) of axial height change, another one has and contacts with described adjusting range (25) linkage portion coordinated, described exhaust gas bypass valve (26) can be driven to move axially along described regulating valve (5) and open when described regulating valve (25) rotates.

6. the variable cross section exhaust gas bypass turbo machine as described in claim 4 or 5, it is characterized in that, the axial height of described adjusting range (25) is around the center of rotation spiral of described regulating valve (5), and described linkage portion is contact the adjustable lever (28) coordinated with described adjusting range (25).

7. the variable cross section exhaust gas bypass turbo machine as described in claim 4 or 5, it is characterized in that, described adjusting range (25) has along the mild protruding protuberance of described regulating valve (5) sense of rotation, correspondingly in described adjusting range (25), forms recess; Described linkage portion is axial projection (47a), and described axial projection (47a) is when described adjusting range (25) is rotated, and described axial projection (47a) can slip over described recess, described protuberance successively.

8. variable cross section exhaust gas bypass turbo machine as claimed in claim 3, it is characterized in that, described regulating valve (5) is provided with the cam thereupon rotated, and described exhaust gas bypass valve (26) is provided with and can contacts the adjustable lever (28) coordinated with described cam edge.

9. the variable cross section exhaust gas bypass turbo machine as described in any one of claim 2-8, it is characterized in that, also comprise spring (27), when described regulating valve (5) is cancelled with the interlock power of described exhaust gas bypass valve (26), described spring (27) controls described exhaust gas bypass valve (26) and is reset to closed condition.

10. the variable cross section exhaust gas bypass turbo machine as described in any one of claim 2-8, it is characterized in that, also comprise valve base (15), it offers valve base inner flow passage interface (18), valve base outer flow passage interface (19), valve base exhaust gas bypass entrance (23), valve base exhaust gas bypass outlet (20); Described regulating valve (5) and described exhaust gas bypass valve (26) are all located at described valve base (15);

Described valve base (15) is located between the inlet end of described outlet pipe (14) and described turbine case (1).

11. variable cross section exhaust gas bypass turbo machines as described in any one of claim 2-8, it is characterized in that, described exhaust gas bypass valve (26) is directly installed on described turbine case (1), described regulating valve (5) is plugged in described turbine case (1), directly to regulate the air inflow entering described air inlet outer flow passage (2).

12. variable cross section exhaust gas bypass turbo machines as claimed in claim 11, it is characterized in that, described turbo machine is provided with air inlet outer flow passage (2), air inlet inner flow passage (3) and exhaust gas bypass pipeline described in two groups corresponding to six cylinder engine, described regulating valve (5) comprises two valve bodies connected, after plug-in mounting enters described turbine case (1), two described valve body difference, simultaneously correspondences control the air inflow of two described air inlet outer flow passages (2).

13. variable cross section exhaust gas bypass turbo machines as described in any one of claim 1-8, is characterized in that,

Also comprise and be located at described power turbine (31) air inlet endface position and stator supporting disk (30) in the form of a ring;

Described stator supporting disk (30) is furnished with some first guide channels and the second guide channel along its circumferential interval, described first guide channel and described second guide channel have predetermined angle, to enable the waste gas that described air inlet inner flow passage (3) is flowed out be guided to described power turbine (31) through described first guide channel, the waste gas that described air inlet outer flow passage (2) is flowed out can be guided to described power turbine (31) through described second guide channel.

14. variable cross section exhaust gas bypass turbo machines as claimed in claim 13, it is characterized in that, the anchor ring of described stator supporting disk (30) is circumferentially with some stators being raised in described anchor ring, described stator has the guiding gutter (29) of through described stator, to form fluting stator (12);

Passage between adjacent described fluting stator (12) forms described first guide channel, and described guiding gutter (29) forms described second guide channel.

15. variable cross section exhaust gas bypass turbo machines as claimed in claim 13, it is characterized in that, the anchor ring of described stator supporting disk (30) is provided with and is raised in described anchor ring and spaced long stator (32) and short-range missile leaf (33), according to counterclockwise, passage between described long stator (32) to described short-range missile leaf (33) forms described second guide channel, and the passage between described short-range missile leaf (33) to described long stator (32) forms described first guide channel.

16. variable cross section exhaust gas bypass turbo machines as claimed in claim 15, is characterized in that, the arrangement angle B of described long stator (32) is 68 ° ~ 80 °, the arrangement angle A of described short-range missile leaf (33), meet: B-A=0 ° ~ 5 °.

17. 1 kinds meet EGR and to circulate the variable cross section exhaust gas bypass turbo machine of needs, comprise turbine case (1), air inlet inner flow passage (3) and air inlet outer flow passage (2) is provided with in described turbine case (1), air inlet inner flow passage (3) and air inlet outer flow passage (2) adopt non-all-round structure respectively, air inlet inner flow passage bears the air inlet of power turbine 0 ° ~ (150 ~ 230) °, and air inlet outer flow passage bears the air inlet of (150 ~ 230) ° ~ 360 °; Described turbine case is also provided with exhaust gas bypass pipeline in (1), and this exhaust gas bypass pipeline and air inlet outer flow passage (2), air inlet inner flow passage (3) be arranged in parallel, but without power turbine (31).

18. a kind of variable cross section exhaust gas bypass turbo machines meeting EGR circulation needs according to claim 17, it is characterized in that: this turbo machine also comprises power turbine (31), valve base (15), outlet pipe (14) and controls annex, and described turbine case (1), valve base (15), outlet pipe (14) are sealed connected together; The regulating valve (5) of adjustable air inlet outer flow passage (2) charge flow rate is installed in described valve base (15); The other end of regulating valve (5) is provided with adjusting range (25), and adjusting range (25) is spiral-shaped structure, and its axial height helically rises around Pivot Point Center.

19. a kind of variable cross section exhaust gas bypass turbo machines meeting EGR circulation needs according to claim 18, it is characterized in that: the exhaust gas bypass valve (26) being provided with the action that can match with regulating valve (5) in described exhaust gas bypass pipeline, exhaust gas bypass valve (26) is arranged in valve base (15) by exhaust gas by-pass valve axle sleeve (21), spring (27) is installed between exhaust gas bypass valve (26) and exhaust gas by-pass valve axle sleeve (21), exhaust gas bypass valve (26) is provided with the adjustable lever (28) of the action that to match with adjusting range (25) near the side of regulating valve (5), during action, controlling annex drives regulating valve (5) to rotate, while regulating air inlet outer flow passage (2) air inflow, the adjusting range (25) of regulating valve (5) promotes adjustable lever (28), exhaust gas bypass valve (26) is opened, and Compress Spring (27), now, bypass exhaust is discharged from exhaust gas bypass pipeline, when regulating valve (5) return, exhaust gas bypass valve (26) is return under spring (27) elastic force effect, and waste gas is bypass no longer.

20. a kind of variable cross section exhaust gas bypass turbo machines meeting EGR circulation needs according to claim 17, is characterized in that:

Position near power turbine (31) in described turbine case (1) is provided with stator supporting disk (30), stator supporting disk (30) is provided with several flutings stator (12), several flutings stator (12) are evenly distributed ringwise;

Described fluting stator (12) adopts gas-solid combining nozzle form, during low engine speed low-load, turbo machine air inlet inner flow passage (3) works, now the flow inlet angle of air inlet inner flow passage (3) is obtained by formula tan (α)=2 π b/ (A/r), wherein b is turbine inlet width, be definite value, flow inlet angle is determined 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, guarantee that two angles are basically identical, gas 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 turbo machines meeting EGR circulation needs according to claim 20, is characterized in that:

Fluting stator (12) neutral position is provided with guiding gutter (29), the arrangement angle (B) of fluting stator (12) is 68 ° ~ 80 °, two trough rims of guiding gutter (29) carry out rotation acquisition by line of cut (36) around the center of stator supporting disk (30), and the narrowest place of groove width presses 3mm and controls.

22. a kind of variable cross section exhaust gas bypass turbo machines meeting EGR circulation needs according to claim 20, it is characterized in that: fluting stator (12) comprises long stator (32) and short-range missile leaf (33), the length of long stator (32) is greater than the length of short-range missile leaf (33), and long stator (32) and short-range missile leaf (33) interval are arranged; The trailing edge (34) of little stator (33) and the leading edge (35) of long stator (32) keep at a certain distance away in a circumferential direction.