CN202266328U - Pulse supercharging turbine device with variable flow passage - Google Patents
Pulse supercharging turbine device with variable flow passage Download PDFInfo
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- CN202266328U CN202266328U CN2011204045164U CN201120404516U CN202266328U CN 202266328 U CN202266328 U CN 202266328U CN 2011204045164 U CN2011204045164 U CN 2011204045164U CN 201120404516 U CN201120404516 U CN 201120404516U CN 202266328 U CN202266328 U CN 202266328U
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- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The utility model discloses a pulse supercharging turbine device with a variable flow passage, which comprises a scroll casing, wherein the scroll casing is provided with an air inlet and an air outlet, a turbine impeller is installed inside the scroll casing, a turbine shaft is installed on the turbine impeller, a flow passage is arranged inside the scroll casing, a position of the flow passage which is close to the turbine impeller is provided with a blade-free nozzle to be communicated with the flow passage, an intermediate separation plate is arranged inside the flow passage, and the intermediate separation plate divides the flow passage into a left side flow passage and a right side flow passage; an arc pneumatic separation plate is respectively arranged inside the left side and the right side flow passages; one end of the pneumatic separation plate is a fixed end and is fixedly connected with the intermediate separation plate, the other end of the pneumatic separation plate is a leading-out air outlet end and is arranged to the position to be close to the blade-free nozzle. Due to the adoption of the pulse supercharging turbine device, different flow passages of the scroll casing can do work on the turbine impeller within different circumferential ranges, so full-circle airflow of the turbine impeller can be more uniform, and the property of the turbine can be further improved.
Description
Technical field
The utility model relates to a kind of pressurizer of internal combustion engine; Relate in particular to and a kind ofly can effectively take into account the high low speed boost demand of motor; The impulse turbine machine of the long-pending variable runner that is used for vehicle turbocharger that does not wait of cross section of fluid channel belongs to technical field of internal combustion engines.
Background technique
Along with the increasingly stringent of national Abgasgesetz and to the continuous lifting of engine performance demand, to the demands for higher performance of vehicle turbocharger.People are more and more stronger for the demand of the engine supercharger that can take into account the high low-speed performance of motor; In order to satisfy the performance requirement in the full operating mode scope of motor; The variable geometry turbine technology receives increasing attention; Advantages such as wherein variable runner turbine technology is simple in structure because of it, good reliability have obtained using more widely, become the emphasis of domestic and international research and development.
In order to adapt to the high low-load exhaust performance of motor, promote turbine efficiency, on double flow channel turbo machine basis, developed multiple variable-section turbomachine structure; But traditional variable-section turbomachine and the engine exhaust pipe that is complementary with it be independent design often; Mate together that Performance Potential must be affected, traditional variable-section turbomachine valve is arranged on spiral case inside, and the valve place can cause bigger aerodynamic loss; Simultaneously traditional variable-section turbomachine spiral case is because runner is less when mating with multi-cylinder engine; The ability of rationalization's engine exhaust pulse is restricted, and therefore, this design does not realize through engineering approaches and commercialization.
For this reason, the turbosupercharging industry has to develop costliness, complex structure, efficient is higher in middle working zone, and at the lower VNT (variable non-blade nozzle turbosupercharger) of small flow and big flow two ends working efficiency to satisfy the performance requirement of motor.But through application for many years, VNT pressurized machine cost height generally reacts in motor company, and rate of fault is high, and pressurized machine low speed efficient is bad, and hope can solve the problem that the type pressurized machine exists.
Patent CN2010102428627 discloses a kind of pulse pressure-charging turbine plant of variable runner; But the outer flow passage structure of this device and inlet guide tube shape change greatly, cause certain loss in efficiency, simultaneously because the non-blade nozzle space is narrow and small; Make the working efficiency circle can only be partial to some design conditions point; The efficient operation interval is restricted, and control valve Flow characteristics and efficiency characteristic are restricted because of valve mechanism, can not obtain full operating mode high-efficient characteristic fully.
Therefore; The utility model hopes under motor height operating mode, all can effectively organize exhaust pulses from the system perspective design is a kind of; Make full use of the impulse turbine machine system of efficient, the variable runner of high-performance of engine exhaust energy, solve the existing one or more problems of conventional variable section turbomachine structure, VNT structure and patent CN2010102428627.
The model utility content
The problem that the utility model will solve is that a kind of pulse pressure-charging turbine plant that can under motor height operating mode, all can effectively organize the variable runner that utilizes the engine exhaust pulse energy will be provided.
In order to address the above problem, the technological scheme that the utility model adopts is:
A kind of pulse pressure-charging turbine plant of variable runner; Comprise spiral case; Spiral case is provided with suction port and air outlet, and turbine wheel is installed in the spiral case, and turbine shaft is installed on turbine wheel; Said spiral case inside is provided with runner; Said runner is provided with the non-blade nozzle that is communicated with runner near the position of turbine wheel, in said runner, is provided with intermediate clapboard, and said intermediate clapboard is separated into left side runner and right side runner with runner: the pneumatic barrier that in left side runner and right side runner, is respectively equipped with arc; One end of said pneumatic barrier is a fixed end, and is affixed with intermediate clapboard, and the other end is the water conservancy diversion outlet side, is arranged on the position near non-blade nozzle.
Below be the further improvement of the utility model to such scheme:
The internal face that said pneumatic barrier is arranged in the spiral case inner flow passage is 5-10mm at the radial distance near the non-blade nozzle place, gets into turbine wheel smoothly with induced draft.
Further improve: the outlet side of said intermediate clapboard is arrived the distance of non-blade nozzle outlet to the distance of non-blade nozzle exit position less than pneumatic barrier water conservancy diversion outlet side, so that air-flow gets into the non-blade nozzle section smoothly.
Further improve: said pneumatic barrier, intermediate clapboard and the moulding of spiral case integrally casting.
Further improve: the pneumatic barrier that is positioned at the left side runner is separated into spiral case left side outer flow passage and spiral case left side inner flow passage with the left side runner;
The pneumatic barrier that is positioned at the right side runner is separated into spiral case right side outer flow passage and spiral case right side inner flow passage with the right side runner;
Said spiral case left side outer flow passage, spiral case left side inner flow passage, spiral case right side inner flow passage and spiral case right side outer flow passage are communicated with non-blade nozzle respectively.
The specific (special) requirements of the design aerodynamic of said pneumatic barrier, pneumatic barrier is the same with the spiral case inwall to be gradual shrinkage flowing on the direction.The inwall camber line in pneumatic barrier cross section and outer wall camber line all the inwall arc shape with the spiral case cross section are close.
Further improve:
Said spiral case left side outer flow passage, spiral case left side inner flow passage, spiral case right side inner flow passage and spiral case right side outer flow passage are to be arranged side by side in the spiral case.
Further improve:
The sectional area of said spiral case left side inner flow passage is less than the sectional area of spiral case left side outer flow passage;
The sectional area of said spiral case right side inner flow passage is less than the sectional area of spiral case right side outer flow passage;
Spiral case left side inner flow passage and spiral case right side inner flow passage sectional area sum are 1/4-1/2 with the ratio of the total sectional area of spiral case left side outer flow passage, spiral case left side inner flow passage, spiral case right side inner flow passage, spiral case right side outer flow passage.
Further improve:
The outer wall camber line that pneumatic barrier is positioned at spiral case left side outer flow passage, spiral case right side outer flow passage is the 0-10 degree with the inwall camber line that spiral case is positioned at outer flow passage on the left of the spiral case, spiral case right side outer flow passage at the angle near the non-blade nozzle position respectively;
It is the 0-10 degree at the angle near the non-blade nozzle position that said pneumatic barrier is positioned at the spiral case left side inner flow passage and the inwall camber line of spiral case right side inner flow passage and the wall of intermediate clapboard.
Further improve:
When reducing the low operating mode of motor, return loss and windage loss outer flow passage in of exhaust flow from the inner flow passage to the outer flow passage; For the air-flow angle of exhaust flow under the high operating mode of control motor, utilize exhaust energy more fully from spiral case left side outer flow passage and spiral case right side outer flow passage inflow turbine wheel; Because the pneumatic barrier that is provided with receives bigger thermal stress between inside and outside runner,, row's static cascade is set respectively in the complete all scopes near the non-blade nozzle position in spiral case left side outer flow passage and spiral case right side outer flow passage for improving the reliability of pneumatic barrier.
Further improve:
The blade of said static cascade tilts to be installed in the outlet port of spiral case left side outer flow passage and spiral case right side outer flow passage respectively with the non-mode that is uniformly distributed with, and the blade of static cascade is cast on the left of the spiral case on the outer flow passage and spiral case right side outer flow passage inwall.
Further improve:
The suction port place of said spiral case is provided with four spiral cases and enters the hole; The hole is entered in two spiral cases left side and the hole is entered on two spiral case right sides; Said two spiral cases left side is entered the hole and is communicated with spiral case left side outer flow passage, spiral case left side inner flow passage respectively, and two spiral case right sides are entered the hole and are connected with spiral case right side inner flow passage and spiral case right side outer flow passage respectively.
Further improve:
The suction port place of said spiral case is connected with gas exhaust manifold; Be provided with gas exhaust manifold outlet left side runner and gas exhaust manifold outlet right side runner in the said gas exhaust manifold, said gas exhaust manifold outlet left side runner and gas exhaust manifold export the right side runner and enter hole and spiral case right side and enter the hole and be communicated with respectively with on the left of the spiral case.
Further improve:
Position near the gas exhaust manifold outlet in said gas exhaust manifold outlet left side runner and the gas exhaust manifold outlet right side runner is respectively equipped with valve; Said valve adopts wing blade pneumatic paddle structure; Hinged between the tube wall of said valve through valve shaft and gas exhaust manifold, said valve and valve shaft are fixed.
Further improve:
The valve axle center of said valve is positioned on the fitting surface of gas exhaust manifold outlet and spiral case suction port.
Further improve:
The two ends of said valve are combined together with the gas exhaust manifold inwall with near the inwall of the pneumatic barrier of the spiral case inlet position mode with overlap joint respectively.
During the low operating mode operation of motor, valve and gas exhaust manifold inwall closely cooperate together, seal fully to guarantee the spiral case outer flow passage, the air-flow entering outer flow passage of the inner flow passage of avoiding flowing through.
Further improve:
Two runner wall angles of said intermediate clapboard are the 0-10 degree, and the radial distance that pneumatic barrier is positioned at the spiral case inner flow passage is 1/2-2/3 with the ratio that intermediate clapboard is positioned at the radial distance of inner flow passage.
Adopt such scheme, effectively steering flow gets into turbine wheel with suitable flow angle, reduces the flow losses of non-blade nozzle.
The another kind of improvement:
For guaranteeing that inlet stream gets into turbine wheel with suitable flow angle; Reduce to flow through the airflow reflux of spiral case inner flow passage to the spiral case outer flow passage; And reduce the loss that the gas exhaust manifold air-flow of flowing through flows into air-flow in the spiral case runner, and improve intake efficiency, the center of the inside and outside runner of spiral case is further improved; Two runner wall angles of said intermediate clapboard are the 5-20 degree, and the radial distance that said pneumatic barrier is positioned at the spiral case inner flow passage and intermediate clapboard are positioned at the ratio of radial distance of spiral case inner flow passage greater than 1/3.
Further improve:
Said pneumatic barrier is positioned at the straight line type wall of spiral case outer flow passage and spends greater than 150 to the excessive angle of curved wall;
Said pneumatic barrier is positioned at spiral case left side outer flow passage, spiral case right side outer flow passage is the 50-60 degree near the axial angle of straight line type wall and non-blade nozzle outlet port at non-blade nozzle place.
The another kind of improvement:
Is the non-blade nozzle dividing plate of arc at spiral case left side outer flow passage and spiral case right side outer flow passage in the cross section that symmetry is set near the non-blade nozzle position; Said spiral case left side outer flow passage and spiral case right side outer flow passage and the sealing of the corresponding non-blade nozzle of non-blade nozzle dividing plate place, said non-blade nozzle dividing plate and spiral case are cast as one.
Further improve:
The radian of said non-blade nozzle dividing plate is the 0-180 degree, cancels the pairing static cascade that originally was installed on spiral case left side outer flow passage and the spiral case right side outer flow passage inwall of this partition position.
When the high operating mode of motor; Valve open, the air inlet simultaneously of four runners of spiral case, spiral case left side inner flow passage and spiral case right side inner flow passage exit flow are realized 360 degree actings to turbine wheel; Because spiral case outer flow passage aditus laryngis place has carried out the angle reach of 0 degree-180 degree; Spiral case left side outer flow passage and spiral case right side outer flow passage are only interval less than the acting of 360 degree, and air-flow further is squeezed, therefore; Need high rotating speed pressurized machine flowing state in the comprehensive assessment, guarantee high speed pressurized machine output torque and flow efficiency.
When motor hangs down operating mode; Valve closing; Only the left side inner flow passage of spiral case and spiral case right side inner flow passage exit flow are to the full Zhou Zuogong of turbine wheel; Because spiral case left side outer flow passage and spiral case right side outer flow passage are only interval less than the acting of 360 degree, have on spiral case outer flow passage inwall, to be provided with the non-static cascade blade that is uniformly distributed with again, and have avoided the airflow reflux from the spiral case inner flow passage to the spiral case outer flow passage to a certain extent; Effectively reduced the airflow reflux loss, the exhaust pulses energy of motor when having made full use of low operating mode.
Because the reach of spiral case outer flow passage aditus laryngis place angle; Under the state of valve opening; Realized left side inner flow passage, right side inner flow passage, left side outer flow passage and right side outer flow passage purpose, and non-ly be uniformly distributed with the static cascade blade, thereby made the turbine wheel inlet air flow more even through being provided with in the outlet of spiral case outer flow passage in different circumferencial directions actings; When reducing the different runner blending losses of airflow reflux loss and non-blade nozzle, further promote the efficient of turbine wheel.
The another kind of improvement: the radian 0-120 degree of said non-blade nozzle dividing plate, cancel the pairing static cascade that originally was installed on spiral case left side outer flow passage and the spiral case right side outer flow passage inwall of this partition position.
The inside and outside runner of spiral case that is not both that this design improvement scheme and last a kind of improvement project are maximum all is 360 degree actings, the 0-120 degree but aditus laryngis staggers.
When motor operates in the high operating mode scope; Valve open, although the dislocation of the aditus laryngis place of spiral case inner flow passage and spiral case outer flow passage, the exit flow of the inside and outside runner of spiral case all is that turbine wheel is carried out the full week acting of 360 degree; The pulse energy of engine exhaust when effectively having utilized high operating mode; In addition, thereby the non-outer flow passage outlet port static cascade blade that is distributed on has further promoted energy utilization ratio, thereby has effectively improved the efficient of turbine wheel.
Motor operates in when hanging down the operating mode scope; Valve closing; Spiral case left side outer flow passage and spiral case right side outer flow passage stop air inlet, and engine exhaust all flows in spiral case left side inner flow passage and the spiral case right side inner flow passage, and spiral case left side inner flow passage and spiral case right side inner flow passage exit flow are realized the full week acting to turbine wheel; Thereby effectively utilized the exhaust energy under the low operating mode of motor, further improved the efficient of turbine wheel.
The utility model is considered engine exhaust system and turbo machine that on the basis of traditional exhaust manifold and double flow channel spiral case, exhaust passage, the left and right sides and spiral case runner inside are designed according to different working conditions as a system.
During the high operating mode of motor, realize the air inlets simultaneously of inner four runners of spiral case, the pulse energy of engine exhaust when effectively having utilized high operating mode, and further promoted energy utilization ratio through the non-static cascade blade that is uniformly distributed with of outer flow passage outlet.During the low operating mode of motor, only inner two the runner air inlets of spiral case, the exhaust pulses energy of motor when making turbo machine effectively utilize low operating mode.Thereby realized under turbo machine height operating mode, all effectively utilizing the purpose of engine exhaust pulse energy.Because the reach of spiral case runner place aditus laryngis; Two kinds of design proposals of the inside and outside runner dislocation of spiral case; And the corresponding non-static cascade blade structure design that is uniformly distributed with; Realize the purpose that the different runners of spiral case do work to turbine wheel in different circumference range, can make the complete all air-flows of turbine wheel more even, further promoted turbine performance.
Below in conjunction with accompanying drawing and embodiment the utility model is further specified.
Description of drawings
Fig. 1 is the structural representation of variable runner turbo machine among the utility model embodiment 1;
Fig. 2 is the ssembly drawing of variable runner turbo machine and outlet pipe among the utility model embodiment 1;
Fig. 3 is a variable runner turbo machine spiral case external structure among the utility model embodiment 1;
Fig. 4 is the External view of outlet pipe among the utility model embodiment 1;
Fig. 5 is the structural representation of variable runner turbine flow road changes of section among the utility model embodiment 2;
Fig. 6 is the another kind of structural representation that changes in cross section, variable runner turbine flow road among the utility model embodiment 3;
Fig. 7 is the variable runner turbo machine 0-180 degree cross section structure schematic representation among the utility model embodiment 4;
Fig. 8 is the 0-180 degree cross section structure schematic representation among the utility model embodiment 5;
Fig. 9 is the structural representation in the 180-360 degree cross section of variable runner turbo machine among the utility model embodiment 6.
Among the figure: the 1-spiral case; The 2-turbine wheel; The 3-air outlet; The 4-intermediate clapboard; The 5-turbine shaft; The 6-pneumatic barrier; 7-spiral case inwall; 8-spiral case left side outer flow passage; 9-spiral case right side outer flow passage; 10-spiral case left side inner flow passage; 11-spiral case right side inner flow passage; The 12-static cascade; The 13-non-blade nozzle; The 14-gas exhaust manifold; 15-gas exhaust manifold outlet left side runner; 16-gas exhaust manifold outlet right side runner; The 17-valve; The 18-valve shaft; The hole is entered in 19-spiral case left side; The hole is entered on 20-spiral case right side; The 21-control system; 22-non-blade nozzle dividing plate.
Embodiment
The pneumatic barrier 6 that is positioned at the left side runner is separated into spiral case left side outer flow passage 8 and spiral case left side inner flow passage 10 with the left side runner.
The pneumatic barrier 6 that is positioned at the right side runner is separated into spiral case right side outer flow passage 9 and spiral case right side inner flow passage 11 with the right side runner.
One end of said pneumatic barrier 6 is a fixed end, and is affixed with intermediate clapboard 4, and the other end is the water conservancy diversion outlet side, is arranged on the position near non-blade nozzle 13.
The internal face that said pneumatic barrier 6 is arranged in the spiral case inner flow passage is 5-10mm at the radial distance Y near non-blade nozzle 13 places, gets into turbine wheel 2 smoothly with induced draft.
Said spiral case left side outer flow passage 8, spiral case left side inner flow passage 10, spiral case right side inner flow passage 11 and spiral case right side outer flow passage 9 are communicated with non-blade nozzle 13 respectively.
The outlet side of said intermediate clapboard 4 to non-blade nozzle 13 exit positions apart from d1 less than pneumatic barrier 6 water conservancy diversion outlet sides to non-blade nozzle 13 outlet apart from d2.
The outlet side of said intermediate clapboard 4 is 2-5mm to non-blade nozzle 13 exit positions apart from d1, and pneumatic barrier 6 water conservancy diversion outlet sides are 2-15mm to non-blade nozzle 13 outlets apart from d2, so that air-flow gets into 13 sections of non-blade nozzles smoothly.
Said pneumatic barrier 6, intermediate clapboard 4 and spiral case 1 integrally casting moulding.
Said spiral case left side outer flow passage 8, spiral case left side inner flow passage 10, spiral case right side inner flow passage 11 and spiral case right side outer flow passage 9 are to be arranged side by side in the spiral case 1;
The sectional area of said spiral case left side inner flow passage 10 is less than the sectional area of spiral case left side outer flow passage 8;
The sectional area of said spiral case right side inner flow passage 11 is less than the sectional area of spiral case right side outer flow passage 9.
Spiral case left side inner flow passage 10 and spiral case right side inner flow passage 11 sectional area sums are 1/4-1/2 with the ratio of the total sectional area of spiral case left side outer flow passage 8, spiral case left side inner flow passage 10, spiral case right side inner flow passage 11, spiral case right side outer flow passage 9.
In order to guarantee that waste gas has better aerodynamic characteristics in the runner of spiral case 1; The specific (special) requirements of the design aerodynamic of said pneumatic barrier 6; Said pneumatic barrier 6 and spiral case inwall 7 are the same to be gradual shrinkage flowing on the direction, the inwall camber line in pneumatic barrier 6 cross sections and outer wall camber line all the inwall arc shape with spiral case 1 cross section are close.
For effective steering flow gets into turbine wheel 2 with suitable flow angle; Reduce the flow losses of non-blade nozzle 13; Setting outer wall camber line that pneumatic barrier 6 is positioned at spiral case left side outer flow passage 8, spiral case right side outer flow passage 9 is the 0-10 degree with the inwall camber line that spiral case 1 is positioned at spiral case left side outer flow passage 8, spiral case right side outer flow passage 9 at the angle Φ 1 near non-blade nozzle 13 positions respectively, is similar to parallel;
Said pneumatic barrier 6 is positioned at the inwall camber line of spiral case left side inner flow passage 10 and spiral case right side inner flow passage 11 and the wall of intermediate clapboard 4 is the 0-10 degree at the angle Φ 2 near non-blade nozzle 13 positions, is similar to parallel.
When reducing the low operating mode of motor, return loss and windage loss outer flow passage in of exhaust flow from the inner flow passage to the outer flow passage; For the air-flow angle of exhaust flow under the high operating mode of control motor, utilize exhaust energy more fully from spiral case left side outer flow passage and spiral case right side outer flow passage inflow turbine wheel; Because the pneumatic barrier that is provided with receives bigger thermal stress between inside and outside runner; For improving the reliability of pneumatic barrier, row's static cascade 12 is set respectively in the complete all scopes near the non-blade nozzle position in spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9.
The blade of said static cascade 12 tilts to be installed in the outlet port of spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 respectively with the non-mode that is uniformly distributed with, and the blade of static cascade 12 is cast on spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 inwalls.
As shown in Figure 2; The suction port place of said spiral case 1 is provided with four spiral cases and enters the hole; Hole 19 is entered in two spiral cases left side and hole 20 is entered on two spiral case right sides; Said two spiral cases left side is entered hole 19 and is communicated with spiral case left side outer flow passage 8, spiral case left side inner flow passage 10 respectively, and two spiral case right sides are entered hole 20 and are connected with spiral case right side inner flow passage 11 and spiral case right side outer flow passage 9 respectively.
Like Fig. 3, shown in Figure 4; The suction port place of said spiral case 1 is connected with gas exhaust manifold 14; Be provided with gas exhaust manifold outlet left side runner 15 and gas exhaust manifold outlet right side runner 16 in the said gas exhaust manifold 14, said gas exhaust manifold outlet left side runner 15 and gas exhaust manifold outlet right side runner 16 enter hole 19 with the spiral case left side respectively and enter hole 20 with the spiral case right side and be communicated with.
Said gas exhaust manifold outlet left side runner 15 is respectively equipped with valve 17 with gas exhaust manifold outlet right side runner 16 interior positions near the gas exhaust manifold outlet; Said valve 17 adopts wing blade pneumatic paddle structure; Hinged between the tube wall of said valve 17 through valve shaft 18 and gas exhaust manifold 14, said valve 17 is fixing through bolt and valve shaft 18.
For ease of the installation of valve 17 and valve shaft 18, the valve axle center of said valve 17 is positioned on the fitting surface of gas exhaust manifold 14 outlets and spiral case 1 suction port.
The two ends of said valve 17 are combined together with gas exhaust manifold 14 inwalls with near the inwall of the pneumatic barrier 6 at the spiral case 1 entrance location place mode with overlap joint respectively.During the low operating mode operation of motor, valve 17 closely cooperates together with gas exhaust manifold 14 inwalls, seals fully to guarantee the spiral case outer flow passage, and the air-flow of the inner flow passage of avoiding flowing through gets into outer flow passage.
Said valve axle center accounts for the 1/3-1/2 of valve chord length to the distance near exhaust outlet one end.
The said valve shaft 18 externally control of control system 21 drives down valve 17 and rotates around valve shaft 18, said external control system 21 by the engine operating parameter of being monitored according to the unlatching of predefined program control valve 17 or close.
Said gas exhaust manifold 14 outlet walls are connected through bolton with spiral case 1 import wall.
During the high operating mode of motor, valve 17 is opened, and is as indicated with a dotted line in Fig. 4, the air inlets simultaneously of four runners of spiral case; When motor hanged down operating mode, valve 17 was closed, and shown in solid line among Fig. 4, valve 17 steering flows get into spiral case left side inner flow passage 10 and spiral case right side inner flow passage 11 smoothly.
The utility model is realized the air inlets simultaneously of inner four runners of spiral case when the high operating mode of motor, the pulse energy of engine exhaust when effectively having utilized high operating mode, and the further energy utilization ratio that promoted that is provided with through outer flow passage outlet static cascade.
During the low operating mode of motor, only inner two the runner air inlets of spiral case, the exhaust pulses energy of motor when making turbine effectively utilize low operating mode.Thereby realized under motor height operating mode, all effectively utilizing the purpose of engine exhaust pulse energy.The turbo machine of design and the outlet pipe mechanism that is complementary have with it further promoted the engine exhaust energy utilization ratio simultaneously.The variable runner turbine of the type pulse technology is simple, can adopt same type of material and existing casting and processing technique to accomplish.
So that the opposing parallel non-blade nozzle 13 entering turbine wheels 2 that inlet stream requires through meeting special width-diameter ratio (w/h).
Two runner wall angle of said intermediate clapboard 4 are the 0-10 degree, are similar to parallel.
The radial distance h that pneumatic barrier 6 is positioned at the spiral case inner flow passage is 1/2-2/3 with the ratio that intermediate clapboard 4 is positioned at the radial distance H of inner flow passage.
The width-diameter ratio (w/h) of spiral case left side inner flow passage 10, spiral case right side inner flow passage 11 place's non-blade nozzles 13 is 0.05-0.5.
Two runner wall angle β of said intermediate clapboard 4 are set at the 5-20 degree.
The radial distance, d that said pneumatic barrier 6 is positioned at the spiral case inner flow passage and intermediate clapboard 4 are positioned at the ratio of radial distance D of spiral case inner flow passage greater than 1/3.
The straight line type wall that said pneumatic barrier 6 is positioned at the spiral case outer flow passage to the excessive angle γ of curved wall greater than 150 degree.
Said pneumatic barrier 6 is positioned at spiral case left side outer flow passage 8, spiral case right side outer flow passage 9 is the 50-60 degree near the axial angle theta of straight line type wall and non-blade nozzle 13 outlet ports at non-blade nozzle 13 places.
The radian of said non-blade nozzle dividing plate 22 is the 0-180 degree; Being about to spiral case left side outer flow passage 8 moves forward (according to different turbine characteristics with the angle that outer flow passage 9 aditus laryngis places in spiral case right side have carried out the 0-180 degree; The best reach that has provided the 0-180 degree is interval, but must confirm optimum value according to different turbine characteristics.）。Cancel pairing static cascade 12 blades that originally were installed on spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 inwalls of this partition position.
When valve 17 is opened; The air inlet simultaneously of four runners of spiral case; Spiral case left side inner flow passage 10 is realized 360 degree actings to turbine wheel 2 with spiral case right side inner flow passage 11 exit flows; Because spiral case outer flow passage aditus laryngis place has carried out the angle reach of 0-180 degree; The air-flow of two outlets of spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 does work to turbine wheel 2 in 360 cross section radian scopes in non-blade nozzle dividing plate 22 terminal place angle cross section, and spiral case left side outer flow passage 8 is only interval less than the work done of 360 degree with spiral case right side outer flow passage 9.
When valve 17 is closed; Spiral case left side outer flow passage 8 stops air inlet with spiral case right side outer flow passage 9; Engine exhaust all flows in spiral case left side inner flow passage 10 and the spiral case right side inner flow passage 11, and the left side inner flow passage 11 of spiral case and spiral case right side inner flow passage 11 exit flows are to turbine wheel 2 full Zhou Zuogong.
Present embodiment is realized the air inlets simultaneously of inner four runners of spiral case when the high operating mode of motor, the pulse energy of engine exhaust when effectively having utilized high operating mode, and the further energy utilization ratio that promoted that is provided with through outer flow passage outlet static cascade.
When the low operating mode of motor, only inner two the runner air inlets of spiral case, the exhaust pulses energy of motor when making turbine effectively utilize low operating mode.Thereby realized under motor height operating mode, all effectively utilizing the purpose of engine exhaust pulse energy.
Because the aditus laryngis place of spiral case outer flow passage has carried out the reach of best angle; Be implemented under the valve opening and closing two states; Spiral case left side runner and right side runner purpose to the turbine wheel acting in different circumference range; Alleviate the uneven problem of turbine wheel full admission to a certain extent, reduced the Gas Mixing in Cross flow loss of different runner exits simultaneously, further promoted the efficient of turbine wheel.
Turbo machine and the outlet pipe mechanism that is complementary have with it further promoted the engine exhaust energy utilization ratio.The variable runner turbine of the type pulse technology is simple, can adopt same type of material and existing casting and processing technique to accomplish.
Embodiment 5: as shown in Figure 8; Can also in spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9, the non-blade nozzle dividing plate 22 that the cross section is an arc be set near non-blade nozzle 13 positions; Said spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 and the sealing of non-blade nozzle dividing plate 22 corresponding non-blade nozzles 13 places, said non-blade nozzle dividing plate 22 is cast as one with spiral case 1.
The radian 0-120 degree of said non-blade nozzle dividing plate 22 is about to the aditus laryngis place dislocation (0-120 degree) of spiral case left side outer flow passage 8, spiral case right side outer flow passage 9 and spiral case left side inner flow passage 10, spiral case right side inner flow passage 11.Cancel pairing static cascade 12 blades that originally were installed on spiral case left side outer flow passage 8 and spiral case right side outer flow passage 9 inwalls of this partition position.
Different with embodiment 4 is that spiral case left side outer flow passage 8, spiral case right side outer flow passage 9, spiral case left side inner flow passage 10, spiral case right side inner flow passage 11 all are 360 degree actings.Confirm the best angle value of the inside and outside runner aditus laryngis of spiral case place dislocation according to different turbine characteristics.
When motor moves in high operating mode; Valve 17 is opened; The air inlet simultaneously of four runners of spiral case, the aditus laryngis place dislocation (0-120 degree) of spiral case left side outer flow passage 8, spiral case right side outer flow passage 9 and spiral case left side inner flow passage 10, spiral case right side inner flow passage 11, but the exit flow of the inside and outside runner of spiral case all is that turbine wheel 2 is carried out the full week acting of 360 degree; The pulse energy of engine exhaust when effectively having utilized high operating mode; In addition, thereby the non-outer flow passage outlet port static cascade blade that is distributed on has further promoted energy utilization ratio, thereby has effectively improved the efficient of turbine wheel.
Motor operates in when hanging down the operating mode scope; Valve 17 is closed; Spiral case left side outer flow passage 8 stops air inlet with spiral case right side outer flow passage 9, and engine exhaust all flows in spiral case left side inner flow passage 10 and the spiral case right side inner flow passage 11, and spiral case left side inner flow passage 10 is realized doing work in full week to turbine wheel 2 with spiral case right side inner flow passage 11 exit flows; Thereby effectively utilized the exhaust energy under the low operating mode of motor, further improved the efficient of turbine wheel.
Present embodiment is when the high operating mode of motor; The air inlet simultaneously of inner four runners of spiral case; And realize that four runners all are the full Zhou Zuogong of 360 degree, the pulse energy of engine exhaust when effectively having utilized high operating mode, and the further energy utilization ratio that promoted that is provided with through outer flow passage outlet static cascade.
When the low operating mode of motor, only inner two the runner air inlets of spiral case, the exhaust pulses energy of motor when making turbine effectively utilize low operating mode.Thereby realized under motor height operating mode, all effectively utilizing the purpose of engine exhaust pulse energy.
Because the inside and outside runner aditus laryngis of spiral case place has been carried out the dislocation of 0-120 degree; Under the state of valve opening; Realized that left side inner flow passage 11, right side inner flow passage 12, left side outer flow passage 9 and right side outer flow passage 10 are on the different circumferencial directions and the full week acting of 360 degree; Thereby make the turbine wheel inlet air flow more even, when reducing the different runner blending losses of non-blade nozzle, further promote the efficient of turbine wheel.
Claims (21)
1. the pulse pressure-charging turbine plant of a variable runner; Comprise spiral case (1); Spiral case (1) is provided with suction port and air outlet (3), and turbine wheel (2) is installed in the spiral case (1), and turbine shaft (5) is installed on turbine wheel (2); Said spiral case (1) inside is provided with runner; Said runner is provided with the non-blade nozzle (13) that is communicated with runner near the position of turbine wheel (2), in said runner, is provided with intermediate clapboard (4), and said intermediate clapboard (4) is separated into left side runner and right side runner with runner: it is characterized in that:
In left side runner and right side runner, be respectively equipped with the pneumatic barrier (6) of arc;
One end of said pneumatic barrier (6) is a fixed end, and affixed with intermediate clapboard (4), the other end is the water conservancy diversion outlet side, is arranged on the position near non-blade nozzle (13).
2. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 1; It is characterized in that: the internal face that said pneumatic barrier (6) is arranged in the spiral case inner flow passage is 5-10mm at the radial distance of locating near non-blade nozzle (13) (Y), gets into turbine wheel (2) smoothly with induced draft.
3. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 1 and 2 is characterized in that: the outlet side of said intermediate clapboard (4) to the distance (d1) of non-blade nozzle (13) exit position less than the distance (d2) of pneumatic barrier (6) water conservancy diversion outlet side to non-blade nozzle (13) outlet.
4. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 3 is characterized in that: said pneumatic barrier (6), intermediate clapboard (4) and spiral case (1) integrally casting moulding.
5. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 3 is characterized in that:
The pneumatic barrier (6) that is positioned at the left side runner is separated into spiral case left side outer flow passage (8) and spiral case left side inner flow passage (10) with the left side runner;
The pneumatic barrier (6) that is positioned at the right side runner is separated into spiral case right side outer flow passage (9) and spiral case right side inner flow passage (11) with the right side runner;
Said spiral case left side outer flow passage (8), spiral case left side inner flow passage (10), spiral case right side inner flow passage (11) and spiral case right side outer flow passage (9) are communicated with non-blade nozzle (13) respectively.
6. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 5 is characterized in that: said spiral case left side outer flow passage (8), spiral case left side inner flow passage (10), spiral case right side inner flow passage (11) and spiral case right side outer flow passage (9) are to be arranged side by side in the spiral case (1).
7. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 6 is characterized in that:
The sectional area of said spiral case left side inner flow passage (10) is less than the sectional area of spiral case left side outer flow passage (8);
The sectional area of said spiral case right side inner flow passage (11) is less than the sectional area of spiral case right side outer flow passage (9);
The ratio of the total sectional area of spiral case left side inner flow passage (10) and spiral case right side inner flow passage (11) sectional area sum and spiral case left side outer flow passage (8), spiral case left side inner flow passage (10), spiral case right side inner flow passage (11), spiral case right side outer flow passage (9) is 1/4-1/2.
8. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 7 is characterized in that:
The outer wall camber line that pneumatic barrier (6) is positioned at spiral case left side outer flow passage (8), spiral case right side outer flow passage (9) is the 0-10 degree with the inwall camber line that spiral case (1) is positioned at outer flow passage (8) on the left of the spiral case, spiral case right side outer flow passage (9) at the angle (Φ 1) near non-blade nozzle (13) position respectively;
It is the 0-10 degree at the angle (Φ 2) near non-blade nozzle (13) position that said pneumatic barrier (6) is positioned at the spiral case left side inner flow passage (10) and the inwall camber line of spiral case right side inner flow passage (11) and the wall of intermediate clapboard (4).
9. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 8 is characterized in that: in spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) near non-blade nozzle (13)
One row's static cascade (12) is set respectively in complete all scopes of putting.
10. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 9; It is characterized in that: the blade of said static cascade (12) tilts to be installed in the outlet port of spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) respectively with the non-mode that is uniformly distributed with, and the blade of static cascade (12) is cast on the left of the spiral case on the outer flow passage (8) and spiral case right side outer flow passage (9) inwall.
11. the pulse pressure-charging turbine plant according to the described a kind of variable runner of claim (10) is characterized in that:
The suction port place of said spiral case (1) is provided with four spiral cases and enters the hole; Hole (19) is entered in two spiral cases left side and hole (20) is entered on two spiral case right sides; Said two spiral cases left side is entered hole (19) and is communicated with spiral case left side outer flow passage (8), spiral case left side inner flow passage (10) respectively, and two spiral case right sides are entered hole (20) and are connected with spiral case right side inner flow passage (11) and spiral case right side outer flow passage (9) respectively.
12. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 11 is characterized in that:
The suction port place of said spiral case (1) is connected with gas exhaust manifold (14); Be provided with gas exhaust manifold outlet left side runner (15) and gas exhaust manifold outlet right side runner (16) in the said gas exhaust manifold (14), said gas exhaust manifold outlet left side runner (15) and gas exhaust manifold export right side runner (16) and enter hole (19) and spiral case right side and enter hole (20) and be communicated with respectively with on the left of the spiral case.
13. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 12 is characterized in that:
Position near the gas exhaust manifold outlet in said gas exhaust manifold outlet left side runner (15) and the gas exhaust manifold outlet right side runner (16) is respectively equipped with valve (17); Said valve (17) adopts wing blade pneumatic paddle structure; Hinged between the tube wall of said valve (17) through valve shaft (18) and gas exhaust manifold (14), said valve (17) is fixing with valve shaft (18).
14. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 13 is characterized in that:
The valve axle center of said valve (17) is positioned on the fitting surface of gas exhaust manifold (14) outlet and spiral case (1) suction port.
15. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 14 is characterized in that:
The two ends of said valve (17) are combined together with gas exhaust manifold (14) inwall with near the inwall of the pneumatic barrier (6) at spiral case (1) the entrance location place mode with overlap joint respectively.
16. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 15 is characterized in that:
Two runner wall angles of said intermediate clapboard (4) are the 0-10 degree, and the radial distance (h) that pneumatic barrier (6) is positioned at the spiral case inner flow passage is 1/2-2/3 with the ratio that intermediate clapboard (4) is positioned at the radial distance (H) of inner flow passage.
17. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 15 is characterized in that:
Two runner wall angles of said intermediate clapboard (4) are the 5-20 degree, and said pneumatic barrier (6) is positioned at the ratio of the radial distance (d) of spiral case inner flow passage and the radial distance (D) that intermediate clapboard (4) is positioned at the spiral case inner flow passage greater than 1/3.
18. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 17 is characterized in that:
Said pneumatic barrier (6) is positioned at the straight line type wall of spiral case outer flow passage and spends greater than 150 to the excessive angle (γ) of curved wall;
It is the 50-60 degree that said pneumatic barrier (6) is positioned at straight line type wall and the axial angle in non-blade nozzle (13) outlet port (θ) that spiral case left side outer flow passage (8), spiral case right side outer flow passage (9) locate near non-blade nozzle (13).
19. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 15 is characterized in that:
Is the non-blade nozzle dividing plate (22) of arc at spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) in the cross section that symmetry is set near non-blade nozzle (13) position; Said spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) are located sealing with the corresponding non-blade nozzle of non-blade nozzle dividing plate (22) (13), and said non-blade nozzle dividing plate (22) is cast as one with spiral case (1).
20. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 19 is characterized in that:
The radian of said non-blade nozzle dividing plate (22) is the 0-180 degree, cancels the pairing static cascade (12) that originally was installed on spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) inwall of this partition position.
21. the pulse pressure-charging turbine plant of a kind of variable runner according to claim 19; It is characterized in that: the radian 0-120 degree of said non-blade nozzle dividing plate (22), cancel the pairing static cascade (12) that originally was installed on spiral case left side outer flow passage (8) and spiral case right side outer flow passage (9) inwall of this partition position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011204045164U CN202266328U (en) | 2011-10-21 | 2011-10-21 | Pulse supercharging turbine device with variable flow passage |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011204045164U CN202266328U (en) | 2011-10-21 | 2011-10-21 | Pulse supercharging turbine device with variable flow passage |
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| Publication Number | Publication Date |
|---|---|
| CN202266328U true CN202266328U (en) | 2012-06-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011204045164U Withdrawn - After Issue CN202266328U (en) | 2011-10-21 | 2011-10-21 | Pulse supercharging turbine device with variable flow passage |
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| CN (1) | CN202266328U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102337961A (en) * | 2011-10-21 | 2012-02-01 | 康跃科技股份有限公司 | Pulse supercharging turbine device with variable flow channel |
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2011
- 2011-10-21 CN CN2011204045164U patent/CN202266328U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102337961A (en) * | 2011-10-21 | 2012-02-01 | 康跃科技股份有限公司 | Pulse supercharging turbine device with variable flow channel |
| CN102337961B (en) * | 2011-10-21 | 2013-03-27 | 康跃科技股份有限公司 | Pulse supercharging turbine device with variable flow channel |
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