CN102080578B - Compound turbo supercharging device having variable cross-section axial radial flows - Google Patents
Compound turbo supercharging device having variable cross-section axial radial flows Download PDFInfo
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- CN102080578B CN102080578B CN201110005183.2A CN201110005183A CN102080578B CN 102080578 B CN102080578 B CN 102080578B CN 201110005183 A CN201110005183 A CN 201110005183A CN 102080578 B CN102080578 B CN 102080578B
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- 150000001875 compounds Chemical class 0.000 title claims abstract description 12
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 239000002131 composite material Substances 0.000 claims description 15
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 210000000867 larynx Anatomy 0.000 abstract 3
- 239000007789 gas Substances 0.000 description 23
- 230000001276 controlling effect Effects 0.000 description 14
- 239000002912 waste gas Substances 0.000 description 11
- 238000000034 method Methods 0.000 description 7
- 238000005266 casting Methods 0.000 description 4
- 230000006872 improvement Effects 0.000 description 4
- 239000000567 combustion gas Substances 0.000 description 3
- 230000007812 deficiency Effects 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000004043 responsiveness Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000009711 regulatory function Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/026—Scrolls for radial machines or engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Supercharger (AREA)
Abstract
The invention discloses a compound turbo supercharging device having variable cross-section axial radial flows, which comprises a double-flow channel volute, wherein the double-flow channel volute is provided with an axial flow channel and a radial flow channel; the axial flow channel and the radial flow channel are respectively provided with a volute nozzle connected to a volute outlet cylinder; a sliding slot is arranged on the double-flow channel volute close to the position of the volute nozzle of the radial flow channel; a slideable moveable larynx baffle is arranged in the sliding slot; and the moveable larynx baffle is in transmission connection with a moveable larynx baffle control mechanism. According to the invention, the variable cross-section function can be realized by using the compound turbo supercharging device, the problems that a blade type variable cross-section turbo supercharger has high cost, low speed and efficiency, inferior reliability, complex structure of a two-stage supercharger and high cost are solved, and the efficiency of a turbo when an engine runs in a low speed is effectively increased while the efficiency is ensured when the engine runs under the large flow working condition.
Description
Technical field
The present invention relates to a kind of turbo charging installation, relate to specifically a kind of variable section axial flow compound turbocharging device, can effectively take into account the high low speed supercharging requirement of motor, belong to field of internal combustion engine.
Background technique
Pressurized machine is widely used Modern Engine, and in order to meet performance and the emission request of motor under all operating modes, pressurized machine must have the adjustable function of boost pressure and discharge pressure.Along with the enforcement of state's four Abgasgesetzs, pressure booster with variable cross section and two-stage supercharger have been called the emphasis of the domestic and international industry research and development of industry.
Generally adopt at present the requirement of at spiral case nozzle place, rotation blade being installed and meeting variable cross section, compared with traditional pressurized machine, it can effectively widen the matching range of pressurized machine and motor, realizes the regulatory function of pressurized machine to boost pressure and discharge pressure.
Rotary vane type variable-area turbocharger structural representation as shown in Figure 1, divide and comprise spiral case 3, spiral case nozzle 5, turbine wheel 7 three parts by the turbine portion of rotary vane type variable-area turbocharger.The aperture that driving mechanism 2 is arranged on the nozzle vane 6 on nozzle ring supporting disk 4 by adjusting regulates the circulation area of nozzle and the angle of outlet waste gas, makes high-temp waste gas peace blow to turbine wheel 7 according to the air-flow angle of design, promotes turbine wheel 7 High Rotation Speeds.Rotor shaft 8 drives compressor impeller 9 High Rotation Speeds in compressor casing 1, and the air that axially enters gas compressor is compressed, and the collection that the air after compression entered compressor casing is sent to participation burning in cylinder.
Rotary vane type pressure booster with variable cross section can be according to the different operating modes of motor, regulate in real time the aperture of nozzle vane 6 to change the circulation area of spiral case nozzle, to meet the performance requirement of motor.Driving mechanism 2 is simple to the adjusting of nozzle vane 6, be easy to control.But in actual application, find that rotary vane type variable-area turbocharger exists some shortcomings:
When motor is under large flow rate working conditions, nozzle vane 6 is nearer apart from turbine blade leading edge, and exhaust gas particle can cause larger wearing and tearing to nozzle vane 6.When motor is under low flow rate condition, nozzle vane 7 is far away apart from turbine blade leading edge, and at this moment the circumferential speed of high temperature gas flow is larger, and turbine becomes action turbine, and in gas flow process, aerodynamic loss is also more serious in addition, makes the decrease in efficiency of pressurized machine.
The waste gas of motor is arranged temperature greatly about 650～850 degree left and right, and has the trend of further rising.Turbocharger operation environment is severe, and strong vibration has very high requirement to the reliability of driving mechanism 2.And the poor problem of the reliability of driving mechanism 2 is not also well solved till now.
The cost of rotary vane type pressure booster with variable cross section is very high, and this makes many motors producer hang back to its expensive price.Cost and life-span have also been limited the market of the type pressure booster with variable cross section.
Adopt two-stage supercharging low pressure turbocharger and high pressure turbocharger co-operation realize the object of engine booster, and describing in detail and please refer to publication number CN 101600869A denomination of invention is two-stage supercharging type exhaust turbo supercharger.Adopting two-stage supercharging is in fact also the pressurized machine co-operation that adopts two configuration different sizes and characteristic, its turbo machine is furnished with spiral case and the turbine of two kinds of different negotiabilities, belong to the pressurized machine of flow-passage-changeable cross section and two kinds of flow characteristics turbines, it can realize higher pressure ratio, reliability pressure ratio high and every one-level turbosupercharger is lower, makes single-stage compressor have wider high efficiency region, but major defect is that coupling, control are complicated, bulk is larger, and cost is higher.
Summary of the invention
The defect that the problem to be solved in the present invention is, poor reliability low for rotary vane type variable-area turbocharger cost high, low speed efficiency and two-stage supercharger complex structure, cost is high, provide a kind of simple in structure, cost is low, reliability is high, and under small flow, has greater efficiency and take into account simultaneously the complex turbine device with variable section of large flow rate working conditions efficiency and flow characteristics.
In order to address the above problem, the present invention by the following technical solutions:
A kind of variable section axial flow compound turbocharging device, comprise double flow channel spiral case, double flow channel spiral case is provided with axial flow runner and runoff runner, on described axial flow runner and runoff runner, be respectively equipped with the spiral case nozzle being communicated with spiral case gas outlet, on described double flow channel spiral case, the position of the spiral case nozzle of close runoff runner is provided with chute, in chute, be provided with slidably mobile aditus laryngis baffle plate, mobile aditus laryngis baffle plate is connected with mobile aditus laryngis baffle plate control mechanism.
Below further improvement of these options of the present invention:
Described runoff runner is positioned at the side near spiral case gas outlet, and axial flow runner is positioned at the side away from spiral case gas outlet, between described runoff runner and axial flow runner, is provided with midfeather.
Further improve:
Described mobile aditus laryngis baffle plate control mechanism comprises final controlling element, be connected to shift fork ring in the outer cover of spiral case gas outlet, described mobile aditus laryngis baffle plate is fixedly connected with shift fork ring, and final controlling element push rod is installed on described final controlling element, between final controlling element push rod and shift fork ring, is connected with shift fork.
Mobile aditus laryngis baffle plate control mechanism is by controlling the switch that moves axially to realize runoff runner of described mobile aditus laryngis baffle plate, and while ensureing axial flow turbine work, combustion gas does not enter runoff spiral casing flow passage, to reduce eddy current loss.
Further improve:
In double flow channel spiral case, be provided with composite turbine impeller, described composite turbine impeller comprises one-level turbine wheel and two-stage turbine impeller.
Described Turbine Blade and described two-stage turbine impeller blade can be set to different numbers according to the performance requirement of pressurized machine with from the requirement of Engine Matching, to meet performance requirement and the emission request of motor.
Further improve:
Described one-level turbine wheel is made up of prismatic blade, and two-stage turbine impeller is made up of the centripetal blade of turbine, and one-level turbine wheel matches with axial flow runner, and two-stage turbine impeller matches with runoff runner.
Further improve:
Dividing plate is installed in described runoff runner, and runoff runner is divided into two runners by dividing plate, forms three air inlet runners with axial flow runner.
Another kind of improvement:
In axial flow runner and runoff runner, dividing plate is installed respectively, axial flow runner and runoff runner are respectively divided into two runners.
Dividing plate is set and can better utilizes waste gas pulse energy, make Pulse wave at less spatial, pulse energy reduces, improve the efficiency of turbine, improve to a certain extent the problem of motor supercharging deficiency in the time of low speed, the while has effectively been taken into account the efficiency of the large flow rate working conditions of motor and has reduced the discharge of motor.
Further improve:
Spiral case nozzle location at axial flow runner is installed guide-ring, and guide-ring tilts to one-level turbine wheel sense of rotation, to control turbine air inlet angle, improves turbine efficiency.
Another kind of improvement:
Described one-level turbine wheel and two-stage turbine impeller interval arrange, there is gap between the two, on midfeather, the position corresponding with this gap arranges annular cavity, and one week stator blade is evenly installed in annular cavity, and described stator blade is between one-level turbine wheel and two-stage turbine impeller.
The mobile upset that stator blade can reduce one-level turbine wheel and two-stage turbine impeller air-flow is to a certain extent set, reduces the energy loss of gas in impeller.
The single-stage expansion of axial flow turbine is than little, and inlet loss is little, and efficiency is higher, but and the single-stage expansion of radial-flow turbine is more on the low side than large efficiency.
The present invention adopts by the double flow channel spiral case forming of axial flow runner and runoff runner sequential working together with the composite turbine impeller being made up of with two-stage turbine impeller one-level turbine wheel, both met the performance requirement under the little load of low engine speed, and can meet again under the large flow rate working conditions of motor and make turbine there is larger negotiability and higher efficiency.
The range of flow of axial flow turbine is wide, and axial flow turbine has higher efficiency under large flow, and the range of flow of radial-flow turbine is narrow, but higher in the efficiency of small flow scope.Adopting after composite turbine, after employing composite turbine, just can ensure that pressurized machine can have higher efficiency under small flow and large flow, meets the job requirement of each operating mode of motor.
Motor is under low flow rate condition, axial flow runner air intake valve is closed, runoff runner air intake valve is opened, and mobile aditus laryngis baffle plate midfeather one side shifting dorsad under the drive of mobile aditus laryngis baffle plate control mechanism now, makes mobile aditus laryngis baffle plate in opening state.The waste gas that motor is discharged only does work to two-stage turbine impeller through runoff runner, because radial-flow turbine has higher efficiency at small flow, can meet the supercharging requirement of the little load of low engine speed.Widen the range of flow of radial-flow turbine, just need larger turbine diameter, when adopting after diameter of axle stream composite turbine device, can reduce on the whole the diameter of turbine, make turbine structure compacter, improve the responsiveness of pressurized machine, reduce the impact of supercharging sluggishness.
Motor is under large flow rate working conditions, runoff runner air intake valve is closed, axial flow runner air intake valve is opened, and now mobile aditus laryngis baffle plate under the drive of mobile aditus laryngis baffle plate control mechanism towards midfeather one side shifting, make mobile aditus laryngis baffle plate in closed condition, during with the work of guarantee axial flow runner, combustion gas does not enter runoff runner, reduces the flow losses of turbine.The waste gas that motor is discharged only does work to one-level turbine wheel through axial flow runner, turbine inlet loss reduces, the range of flow of axial flow turbine is wide, under large flow, there is higher efficiency, can meet motor and make the larger negotiability of having of turbine and there is higher efficiency under large flow rate working conditions.
Channel turbine worm frame in the present invention is simple, inheritance good, qualified casting is higher; Composite turbine impeller in the present invention can obtain higher pneumatic efficiency and higher structural strength by analysis and the optimization of modern CFD, FEA technology; Complex turbine device with variable section in the present invention can adopt existing casting and process equipment to produce, and cost is low and easily realize fast through engineering approaches.
The present invention adopts composite turbine device can realize variable cross section function, effectively solved that leaf formula variable-area turbocharger cost high, low speed efficiency is low, poor reliability and two-stage supercharger complex structure, problem that cost is high, the efficiency of turbine while effectively improving low engine speed, efficiency while effectively having taken into account the large flow rate working conditions of motor simultaneously.
Below in conjunction with drawings and Examples, patent of the present invention is further described:
Brief description of the drawings
Accompanying drawing 1 is the structural representation of the rotary vane type variable-area turbocharger in background technique of the present invention;
Accompanying drawing 2 is structural representations of the complex turbine device with variable section in the embodiment of the present invention 1;
Accompanying drawing 3 is structural representations of air intake valve control mechanism in the embodiment of the present invention 1;
Accompanying drawing 4 is structural representations of complex turbine device with variable section under low flow rate condition in the embodiment of the present invention 1;
Accompanying drawing 5 is structural representations of complex turbine device with variable section under large flow rate working conditions in the embodiment of the present invention 1;
Accompanying drawing 6 is structural representations of the embodiment of the present invention 2;
Accompanying drawing 7 is structural representations of the embodiment of the present invention 3;
Accompanying drawing 8 is structural representations of the embodiment of the present invention 4;
Accompanying drawing 9 is structural representations of the embodiment of the present invention 5;
Accompanying drawing 10 is structural representations of the embodiment of the present invention 6;
Accompanying drawing 11 is structural representations of the embodiment of the present invention 7.
In figure: 1-compressor casing; 2-driving mechanism; 3-spiral case; 4-nozzle ring supporting disk; 5-spiral case nozzle; 6-nozzle vane; 7-turbine wheel; 8-rotor shaft; 9-compressor impeller; 10-double flow channel spiral case; 11-axial flow runner; 12-runoff runner; 13-composite turbine impeller; 14-one-level turbine wheel; 15-two-stage turbine impeller; 16-midfeather; 17-moves aditus laryngis baffle plate; 18-final controlling element; 19-final controlling element push rod; 20-shift fork; 21-shift fork ring; 22-actuator bracket; 23-fixed rotating shaft; 24-spiral case gas outlet; 25-axial flow runner air intake valve; 26-runoff runner air intake valve; 27-air intake valve control mechanism; 28-dividing plate; 29-guide-ring; 30-stator blade.
Embodiment
Embodiment 1: as shown in accompanying drawing 2 and accompanying drawing 3, a kind of variable section axial flow compound turbocharging device, comprises double flow channel spiral case 10, is provided with composite turbine impeller 13 and rotor shaft 8 in double flow channel spiral case 10; On described double flow channel spiral case 10, be connected with spiral case gas outlet 24; Double flow channel spiral case 10 is provided with axial flow runner 11 and runoff runner 12, is respectively equipped with the spiral case nozzle 5 being communicated with spiral case gas outlet 24 on described axial flow runner 11 and runoff runner 12.
Described runoff runner 12 is positioned at the side near spiral case gas outlet 24, and axial flow runner 11 is positioned at the side away from spiral case gas outlet 24, between described runoff runner 12 and axial flow runner 11, is provided with midfeather 16.
Described runoff runner 12 is provided with runoff runner air intake valve 26, axial flow runner 11 is provided with axial flow runner air intake valve 25, described runoff runner air intake valve 26 and axial flow runner air intake valve 25 are in transmission connection with air intake valve control mechanism 27 respectively, and air intake valve control mechanism 27 is realized axial flow runner 11 and the sequential working of runoff runner 12 under motor different flow operating mode by the switching of controlling axial flow runner air intake valve 25 and runoff runner air intake valve 26.
Described composite turbine impeller 13 comprises one-level turbine wheel 14 and two-stage turbine impeller 15, wherein one-level turbine wheel 14 is made up of prismatic blade, two-stage turbine impeller 15 is made up of the centripetal blade of turbine, one-level turbine wheel 14 matches with axial flow runner 11, and two-stage turbine impeller 15 matches with runoff runner 12.
On described double flow channel spiral case 10, the position of the spiral case nozzle 5 of close runoff runner 12 is provided with chute, is provided with slidably mobile aditus laryngis baffle plate 17 in chute, and mobile aditus laryngis baffle plate 17 is connected with mobile aditus laryngis baffle plate control mechanism.
Described mobile aditus laryngis baffle plate control mechanism comprises final controlling element 18, and described final controlling element 18 is fixedly supported on double flow channel spiral case 10 by actuator bracket 22.
Be connected to shift fork ring 21 in the outer cover of spiral case gas outlet 24, described mobile aditus laryngis baffle plate 17 is fixedly connected with shift fork ring 21.
On described final controlling element 18, final controlling element push rod 19 is installed, between final controlling element push rod 19 and shift fork ring 21, be connected with shift fork 20, shift fork 20 one end are fixedly connected with shift fork ring 21, the other end is fixedly connected with by rotating shaft with final controlling element push rod 19, and the intermediate portion of shift fork 20 is rotationally connected by fixed rotating shaft 23 and actuator bracket 22.
As shown in accompanying drawing 3 and accompanying drawing 4, motor is under low flow rate condition, air intake valve control mechanism 27 controls axial flow runner air intake valve 25 and cuts out, runoff runner air intake valve 26 is opened, and now mobile aditus laryngis baffle plate 17 midfeather 16 1 side shiftings dorsad under the drive of mobile aditus laryngis baffle plate control mechanism 18, make mobile aditus laryngis baffle plate 17 in opening state.
The waste gas that motor is discharged only does work to two-stage turbine impeller 15 through runoff runner 12, because radial-flow turbine has higher efficiency at small flow, can meet the supercharging requirement of the little load of low engine speed.And adopt after diameter of axle stream composite turbine device, can reduce on the whole the diameter of turbine, make turbine structure compacter, improve the responsiveness of pressurized machine, reduce the impact of supercharging sluggishness.
As shown in accompanying drawing 3 and accompanying drawing 5, motor is under large flow rate working conditions, air intake valve control mechanism 27 regulated flow runner air intake valves 26 are closed, axial flow runner air intake valve 25 is opened, and now mobile aditus laryngis baffle plate 17, towards midfeather 16 1 side shiftings under the drive of mobile aditus laryngis baffle plate control mechanism 18, makes mobile aditus laryngis baffle plate 17 in closed condition, to ensure axial flow runner when work, combustion gas does not enter runoff runner, reduces the flow losses of turbine.The waste gas that motor is discharged only does work to one-level turbine wheel 14 through axial flow runner 11, turbine inlet loss reduces, the range of flow of axial flow turbine is wide, under large flow, there is higher efficiency, can meet motor and make the larger negotiability of having of turbine and there is higher efficiency under large flow rate working conditions.
Patent of the present invention is the demand to variable-area turbocharger for motor, complete the exploitation of complex turbine device with variable section, adopt the compound mode of two-stage turbine, turbine efficiency while having improved low engine speed, and low speed torque and the output power of motor are improved, improve the booster response characteristic of motor, taken into account the boost demand under low engine speed and high speed operating mode simultaneously.The type complex turbine device with variable section can adopt the casting of existing common pressurized machine and processing technique to complete.
In above-described embodiment, spiral case gas outlet 24 can also be made to packaged type, motor is under low flow rate condition, by regulating the axial position of spiral case gas outlet 24, meet the negotiability of radial-flow turbine, realize and the matched well of motor under low flow rate condition.
Embodiment 2: as shown in Figure 6, in order reasonably to utilize pulse energy, can also, on embodiment 1 basis, at axial flow runner 11 and the interior dividing plate 28 of installing respectively of runoff runner 12, axial flow runner 11 and runoff runner 12 be respectively divided into two runners.
Dividing plate 28 is cast as one with double flow channel spiral case 10.Respectively be installed into air valve in four runner imports that are divided into by dividing plate 28, reasonably utilize waste gas pulse energy by the switching of the each air intake valve of air intake valve control mechanism control.
After adopting this kind of technological scheme, can better utilize waste gas pulse energy, make Pulse wave at less spatial, pulse energy reduces, improve the efficiency of turbine, improve to a certain extent the problem of motor supercharging deficiency in the time of low speed, can effectively take into account the negotiability of large flow rate working conditions turbine and the efficiency of raising turbine simultaneously.
Embodiment 3, as shown in Figure 7, in order reasonably to utilize pulse energy, can also be on embodiment 1 basis, only, at the interior installation dividing plate 28 of runoff runner 12, runoff runner 12 is divided into two runners by dividing plate 28, forms three air inlet runners with axial flow runner 11, three air inlet runners at double flow channel spiral case are respectively installed into air valve, the performance requirement while meeting the each operating mode of motor by the switching of the each air intake valve of air intake valve control mechanism control.
Under low flow rate condition, runoff runner 12 is installed after dividing plate 28, can effectively utilize waste gas pulse energy, improves the efficiency of turbine, improves the problem of low engine speed supercharging deficiency.
Under large flow rate working conditions, the range of flow of axial flow turbine is wider, and efficiency is higher, can meet the turbine negotiability of motor under large flow rate working conditions.And compared with the present embodiment 2, adopt less an air intake valve control mechanism at axial flow runner, composite turbine apparatus structure is become simple, operation more easily realizes.
Embodiment 4: as shown in Figure 8, can also be on embodiment 1 basis, guide-ring 29 is installed in spiral case nozzle 5 positions at axial flow runner 11, and guide-ring 29 tilts to one-level turbine wheel 14 sense of rotation, to ensure that air-flow direction is according to the rules blown into one-level turbine wheel 14.Adopt the utilization that can improve motor exhaust energy to axial flow runner 11 in the time of high speed after this kind of technological scheme, improved turbine efficiency, meet the requirement of the large flow rate working conditions of motor.
Embodiment 5: can also be on embodiment 2 basis, as shown in Figure 9, guide-ring 29 is installed in spiral case nozzle 5 positions at axial flow runner 11, and guide-ring 29 tilts to one-level turbine wheel 14 sense of rotation, to ensure that air-flow direction is according to the rules blown into one-level turbine wheel 14.
Adopt the utilization that can improve motor exhaust energy to axial flow runner 11 in the time of high speed after this kind of technological scheme, improved turbine efficiency, meet the requirement of the large flow rate working conditions of motor.
Embodiment 6: as shown in Figure 10, can also be on embodiment 5 basis, one-level turbine wheel 14 and two-stage turbine impeller 15 are designed to independent two-part, do not connect together, between two impellers, be provided with certain gap, on midfeather 16, the position corresponding with this gap arranges annular cavity, and one week stator blade 30 evenly installing in annular cavity, in the gap of described stator blade 30 between one-level turbine wheel 14 and two-stage turbine impeller 15.
Under the large flow rate working conditions of motor, reduce the gas that one-level turbine wheel 14 is done work and flow into two-stage turbine impeller 15, under motor low flow rate condition, reduce the gas that two-stage turbine impeller 15 is done work and flow into one-level turbine wheel 14, reduce to a certain extent the mobile upset of air-flow in impeller, reduce the energy loss of gas in impeller.
Stator blade 30 has certain gap apart from rotor shaft wheel hub diametrically, to ensure that one-level turbine wheel 14 and two-stage turbine impeller can rotate normally, can not snap into stator blade 30, stator blade 30 use flange plate are bolted to meet the structural strength requirement of double flow channel spiral case 10.
Embodiment 7: as shown in Figure 11, can also be on embodiment 3 basis, one-level turbine wheel 14 and two-stage turbine impeller 15 are designed to independent two-part, do not connect together, between two impellers, be provided with certain gap, on midfeather 16, the position corresponding with this gap arranges annular cavity, and one week stator blade 30 evenly installing in annular cavity, in the gap of described stator blade 30 between one-level turbine wheel 14 and two-stage turbine impeller 15.
Under the large flow rate working conditions of motor, reduce the gas that one-level turbine wheel 14 is done work and flow into two-stage turbine impeller 15, under motor low flow rate condition, reduce the gas that two-stage turbine impeller 15 is done work and flow into one-level turbine wheel 14, reduce to a certain extent the mobile upset of air-flow in impeller, reduce the energy loss of gas in impeller.
Patent of the present invention is the demand to variable-area turbocharger for motor, complete the exploitation of complex turbine device with variable section, adopt the compound mode of two-stage turbine, turbine efficiency while having improved low engine speed, and low speed torque and the output power of motor are improved, improve the booster response characteristic of motor, taken into account the boost demand under low engine speed and high speed operating mode simultaneously.The type complex turbine device with variable section can adopt the casting of existing common pressurized machine and processing technique to complete.
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 (3)
1. a variable section axial flow compound turbocharging device, comprise double flow channel spiral case (10), double flow channel spiral case (10) is provided with axial flow runner (11) and runoff runner (12), on described axial flow runner (11) and runoff runner (12), be respectively equipped with the spiral case nozzle (5) being communicated with spiral case gas outlet (24), it is characterized in that: the position of the upper spiral case nozzle (5) near runoff runner (12) of described double flow channel spiral case (10) is provided with chute, in chute, be provided with slidably mobile aditus laryngis baffle plate (17), mobile aditus laryngis baffle plate (17) is connected with mobile aditus laryngis baffle plate control mechanism,
Described runoff runner (12) is positioned at the side near spiral case gas outlet (24), axial flow runner (11) is positioned at the side away from spiral case gas outlet (24), between described runoff runner (12) and axial flow runner (11), is provided with midfeather (16);
Described mobile aditus laryngis baffle plate control mechanism comprises final controlling element (18), be connected to shift fork ring (21) in the outer cover of spiral case gas outlet (24), described mobile aditus laryngis baffle plate (17) is fixedly connected with shift fork ring (21), final controlling element push rod (19) is installed on described final controlling element (18), between final controlling element push rod (19) and shift fork ring (21), is connected with shift fork (20);
In double flow channel spiral case (10), be provided with composite turbine impeller (13), described composite turbine impeller (13) comprises one-level turbine wheel (14) and two-stage turbine impeller (15);
Described one-level turbine wheel (14) is made up of prismatic blade, two-stage turbine impeller (15) is made up of the centripetal blade of turbine, one-level turbine wheel (14) matches with axial flow runner (11), and two-stage turbine impeller (15) matches with runoff runner (12);
Dividing plate (28) is installed in described runoff runner (12), and runoff runner (12) is divided into two runners by dividing plate (28), forms three air inlet runners with axial flow runner (11);
In axial flow runner (11) and runoff runner (12), dividing plate (28) is installed respectively, axial flow runner (11) and runoff runner (12) are respectively divided into two runners;
Guide-ring (29) is installed in spiral case nozzle (5) position at axial flow runner (11), and guide-ring (29) tilts to one-level turbine wheel (14) sense of rotation.
2. variable section axial flow compound turbocharging device according to claim 1, it is characterized in that: guide-ring (29) is installed in spiral case nozzle (5) position at axial flow runner (11), and guide-ring (29) tilts to one-level turbine wheel (14) sense of rotation.
3. variable section axial flow compound turbocharging device according to claim 2, it is characterized in that: described one-level turbine wheel (14) arranges with two-stage turbine impeller (15) interval, there is gap between the two, in the upper position corresponding with this gap of midfeather (16), annular cavity is set, one week stator blade (30) is evenly installed in annular cavity, and described stator blade (30) is positioned between one-level turbine wheel (14) and two-stage turbine impeller (15).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110005183.2A CN102080578B (en) | 2011-01-12 | 2011-01-12 | Compound turbo supercharging device having variable cross-section axial radial flows |
| PCT/CN2011/000459 WO2012094781A1 (en) | 2011-01-12 | 2011-03-23 | Axial-radial-flow composite turbocharger with a variable section |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110005183.2A CN102080578B (en) | 2011-01-12 | 2011-01-12 | Compound turbo supercharging device having variable cross-section axial radial flows |
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| CN102080578A CN102080578A (en) | 2011-06-01 |
| CN102080578B true CN102080578B (en) | 2014-07-30 |
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| CN201110005183.2A Active CN102080578B (en) | 2011-01-12 | 2011-01-12 | Compound turbo supercharging device having variable cross-section axial radial flows |
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| WO (1) | WO2012094781A1 (en) |
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| CN102661180A (en) * | 2012-05-07 | 2012-09-12 | 康跃科技股份有限公司 | Dual-zone turbine for turbocharging |
| CN103266949B (en) * | 2013-05-16 | 2018-06-15 | 湖南天雁机械有限责任公司 | Turbocharger with lever braking flow-passage-changeable |
| DE102016208160B4 (en) | 2016-05-12 | 2020-04-23 | Continental Automotive Gmbh | Turbine for an exhaust gas turbocharger with a double-flow turbine housing and a valve arrangement with improved outflow |
| CN107100719B (en) * | 2017-04-27 | 2019-06-11 | 同济大学 | An axially variable section turbocharger |
| US11073076B2 (en) | 2018-03-30 | 2021-07-27 | Deere & Company | Exhaust manifold |
| US10662904B2 (en) | 2018-03-30 | 2020-05-26 | Deere & Company | Exhaust manifold |
| CN108894858A (en) * | 2018-06-21 | 2018-11-27 | 浙江吉利控股集团有限公司 | The ternary catalystic device structure of integrated heat-insulation window |
| CN110735673B (en) * | 2019-11-18 | 2021-10-26 | 大连海事大学 | Double-channel volute |
| CN112576317B (en) * | 2020-12-08 | 2023-11-24 | 内蒙古汇能集团蒙南发电有限公司 | Multistage turbine generator |
| CN112922678B (en) * | 2021-02-03 | 2022-08-30 | 东方电气集团东方汽轮机有限公司 | Steam inlet chamber for axial steam outlet of steam turbine |
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Also Published As
| Publication number | Publication date |
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| WO2012094781A1 (en) | 2012-07-19 |
| CN102080578A (en) | 2011-06-01 |
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Denomination of invention: Variable cross-section axial runoff composite turbocharger Effective date of registration: 20220701 Granted publication date: 20140730 Pledgee: Shandong Shouguang Rural Commercial Bank Co.,Ltd. Pledgor: Kangyue Technology (Shandong) Co.,Ltd. Registration number: Y2022980009719 |