CN102733931A - Turbocharger for internal combustion engine - Google Patents
Turbocharger for internal combustion engine Download PDFInfo
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- CN102733931A CN102733931A CN2012100908559A CN201210090855A CN102733931A CN 102733931 A CN102733931 A CN 102733931A CN 2012100908559 A CN2012100908559 A CN 2012100908559A CN 201210090855 A CN201210090855 A CN 201210090855A CN 102733931 A CN102733931 A CN 102733931A
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- 238000002485 combustion reaction Methods 0.000 title abstract 2
- 239000002912 waste gas Substances 0.000 claims abstract description 103
- 238000007599 discharging Methods 0.000 claims description 49
- 238000011144 upstream manufacturing Methods 0.000 claims description 22
- 239000002360 explosive Substances 0.000 claims description 7
- 230000001681 protective effect Effects 0.000 abstract 4
- 230000007704 transition Effects 0.000 abstract 2
- 239000007789 gas Substances 0.000 description 20
- 239000011148 porous material Substances 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 239000007787 solid Substances 0.000 description 3
- 239000000446 fuel Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
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- 230000009467 reduction Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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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
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
The invention provides a turbocharger for an internal combustion engine. In a turbine housing (3), a second discharge outlet (2a) of a second discharge turbine pipe (2) is located at the downstream side of a first discharge outlet (1a) of a first discharge turbine pipe (1) along the flow direction of waste gas in a turbine wheel (4). A protective cover wall of the turbine housing (3) covering a protective cover edge (SE) of the turbine wheel (4) comprises an arc protective cover wall (SW1) with an arc cross section and located in a flow direction transition section of the turbine wheel (4), in the flow direction transition section of the turbine wheel (4), the flow direction of the waste gas changes from a radial direction to an axial direction in the turbine wheel (4). The second discharge outlet (2a) is disposed in the arc protective cover wall (SW1).
Description
Technical field
The present invention relates to a kind of turbosupercharger that is used for explosive motor.
Background technique
The concrete example (referring to for example JP2007-23893A or JP2007-23894A) of the turbosupercharger with two discharging scrolls that formerly proposes will be described with reference to Fig. 9.
The turbosupercharger that formerly proposes that in for example JP2007-23893A or JP2007-23894A, details comprises the first discharging scroll 101 and the second discharging scroll 102.The first discharging scroll 101 comprises the first exhaust outlet 101a, and waste gas is partly exported towards the upstream side that the flow direction of waste gas in the turbine wheel 104 of turbine wheel 104 is positioned at upstream side through the first exhaust outlet 101a.The second discharging scroll 102 comprises the second exhaust outlet 102a, and waste gas is positioned at the part output in the downstream side of the first exhaust outlet 101a towards the flow direction along waste gas of turbine wheel 104 through the second exhaust outlet 102a.
The flow direction that outputs to the waste gas of turbine wheel 104 from the first exhaust outlet 101a becomes axial direction (axial flow) from radial direction (radially inwardly flowing) turbine wheel 104; Afterwards, waste gas is in axial direction exported (referring to the dotted arrow α Fig. 9) from turbine wheel 104.
As shown in Figure 9, the second exhaust outlet 102a offers in the downstream side part that the flow direction of waste gas in the turbine wheel 104 of turbine wheel 104 is arranged in the downstream side.
Particularly, the second exhaust outlet 102a is formed among the cylindrical shroud wall SW102 (barrel surface parallel substantially with the axial direction of turbine wheel 104) in the downstream side part (cover the shroud edge SE100 of turbine wheel 104 and towards the wall surface of downstream side direct exhaust) of the guard shield wall (shroud wall) of turbine shroud 103.
Therefore, shown in the solid arrow β among Fig. 9, the waste gas that outputs to turbine wheel 104 from the second exhaust outlet 102a with converge with the right angle from the exhaust flow of first exhaust outlet 101a output (stream that is directed along the axial direction of turbine wheel 104 substantially).
Therefore, fierce collision from the first exhaust outlet 101a waste gas (the dotted arrow α Fig. 9) that outputs to turbine wheel 104 and the downstream side part of waste gas (the solid arrow β Fig. 9) in turbine wheel 104 that outputs to turbine wheel 104 from the second exhaust outlet 102a.Thereby, shown in the solid arrow γ among Fig. 9, produce powerful turbulent flow in the exhaust flow in the downstream side part in turbine wheel 104.This turbulent flow can be disturbed the rotation of turbine wheel 104, thereby can reduce turbine efficiency.
JP2007-192125A has instructed a kind of turbosupercharger that overcomes above-mentioned shortcoming.
In the turbosupercharger of JP2007-192125A; The outlet bend (deviator) that the flow direction of waste gas is become axial direction is arranged on the downstream of the second exhaust outlet 102a, bumps in the position of converging from the waste gas of first exhaust outlet 101a output and waste gas from second exhaust outlet 102a output of converging with restriction waste gas.
The technology of JP2007-192125A can be at the exhaust flow of exporting from the first exhaust outlet 101a and from realizing the little angle of converging between the exhaust flow of second exhaust outlet 102a output.Yet, owing to be provided with the outlet bend, thus waste gas converge the exhaust outlet of position near turbine wheel 104.Therefore, in turbine wheel 104, do not have just to export from the waste gas of second exhaust outlet 102a output under the well-mixed situation from turbine wheel 104 with the waste gas of exporting from the first exhaust outlet 101a.
Thereby, bump in the outlet port of turbine wheel 104 from the exhaust flow of first exhaust outlet 101a output and the exhaust flow of exporting from the second exhaust outlet 102a.Therefore, in the exhaust flow in the outlet port of turbine wheel 104, produce big turbulent flow.
Turbulent flow in that the outlet port of turbine wheel 104 produces is disturbed the rotation of turbine wheel 104, thereby can reduce turbine efficiency.
Summary of the invention
The present invention has overcome above-mentioned shortcoming.Therefore, the object of the present invention is to provide a kind of turbosupercharger that can be limited in the inside and the outlet port turbulization of turbine wheel and can improve turbine efficiency.
According to the present invention, a kind of turbosupercharger that is used for explosive motor is provided, this turbosupercharger comprises turbine shroud and turbine wheel.Said turbine shroud comprises a plurality of discharging scrolls, and each in said a plurality of discharging scrolls is suitable for producing eddy flow from the waste gas by explosive motor output, and is suitable for the eddy flow of waste gas is discharged into the inboard of turbine shroud.Said turbine wheel is suitable for rotating through the waste gas by the supply of said a plurality of discharging scroll.Said turbine wheel is suitable for discharging the waste gas of being supplied along the radial direction of turbine wheel from the radial outside of turbine wheel by said a plurality of discharging scrolls along the axial direction of turbine wheel.Said a plurality of discharging scroll comprises the first discharging scroll and the second discharging scroll.The said first discharging scroll comprises first exhaust outlet, and waste gas is partly exported towards the upstream side that the flow direction of waste gas in the turbine wheel of turbine wheel is positioned at upstream side through first exhaust outlet.The said second discharging scroll comprises second exhaust outlet, and waste gas is positioned at the part output in the downstream side of first exhaust outlet towards the flow direction along waste gas of turbine wheel through second exhaust outlet.Said turbine shroud comprises the guard shield wall of the shroud edge that covers turbine wheel.Said guard shield wall comprises the arc guard shield wall that flows to changeover portion that has arc section and be arranged in turbine wheel, and flowing in the changeover portion of turbine wheel, the flow direction of waste gas becomes axial direction from radial direction in turbine wheel.Second exhaust outlet is offered in arc guard shield wall.
Description of drawings
Accompanying drawing described here only is for illustration purposes, is not to be intended to limit by any way scope of the present invention.
Figure 1A is the axial, cross-sectional view according to the turbosupercharger of the first embodiment of the present invention;
Figure 1B is the local amplification sectional view of the exhaust gas turbine of the turbosupercharger shown in Figure 1A;
Fig. 2 A is the sectional view of the IIA-IIA line intercepting in Figure 1A;
Fig. 2 B is the sectional view of the IIB-IIB line intercepting in Figure 1A;
Fig. 3 is variable volume valve (volume changeable valve) and the schematic sectional view of exhaust gas bypass reduction valve (wastegate valve) that illustrates according to first embodiment's exhaust gas turbine;
Fig. 4 is the schematic partial section that the exhaust gas turbine of turbosupercharger according to a second embodiment of the present invention is shown;
Fig. 5 is the schematic partial section of exhaust gas turbine that the turbosupercharger of a third embodiment in accordance with the invention is shown;
Fig. 6 is the schematic partial section of exhaust gas turbine that the turbosupercharger of a fourth embodiment in accordance with the invention is shown;
Fig. 7 is the schematic partial section that the exhaust gas turbine of turbosupercharger according to a fifth embodiment of the invention is shown;
Fig. 8 is the schematic partial section that the exhaust gas turbine of turbosupercharger according to a sixth embodiment of the invention is shown;
Fig. 9 is the schematic partial section that the exhaust gas turbine of the turbosupercharger that formerly proposes is shown.
Embodiment
To describe various embodiments of the present invention with reference to accompanying drawing.
Following embodiment is provided, so that the present invention exemplarily to be described, and the invention is not restricted to following embodiment.
Be discussed below in embodiment's the process, in all embodiments, similar assembly is by identical label indication.
(first embodiment)
To the first embodiment of the present invention be described referring to figs. 1 through Fig. 3.
Turbosupercharger is installed to explosive motor (for example, petrol engine, diesel engine).In addition, the type of motor can be any kind (for example, Reciprocating engine, a rotary engine).In addition, in this case, turbosupercharger is installed to the driving motor of vehicle.
Turbosupercharger is a kind of utilization from the energy of the waste gas of engine emission to being introduced in the pressurized machine of the entering air pressurized the motor.Shown in Figure 1A, the turbosupercharger of present embodiment comprises turbine shroud 3, turbine wheel 4, compressor impeller 5, compressor housing 6, axle 7 and bearing support 8.Turbine shroud 3 comprises a plurality of discharging scrolls, is specially the first discharging scroll 1 and the second discharging scroll 2, and each in said a plurality of discharging scrolls is suitable for from the waste gas of motor output, producing eddy flow, and exports the waste gas eddy flow towards the inboard of turbine shroud 3.Turbine wheel 4 is suitable for rotating through the waste gas by the first discharging scroll 1 and 2 supplies of the second discharging scroll.When turbine wheel 4 rotations; Turbine wheel 4 is fed to the waste gas of turbine wheel 4 by the first discharging scroll 1 and the second discharging scroll 2 from the radial outside of turbine wheel 4 along the output of the axial direction of turbine wheel 4, and said axial direction is and the parallel direction of the spin axis of turbine wheel 4 (and therefore being a spin axis of spools 7).Compressor impeller 5 rotates through the rotating force of turbine wheel 4, with to getting into air pressurized.Compressor housing 6 is configured to spiral-shaped, and holds compressor impeller 5.Axle 7 rotations with turbine wheel 4 are transmitted to compressor impeller 5.Bearing support 8 is back shaft 7 rotatably, so that axle 7 can high speed rotating.
Turbosupercharger is constructed such that bearing support 8 in axial direction places between turbine shroud 3 and the compressor housing 6, and bearing support 8, turbine shroud 3 and compressor housing 6 are bonded to together such as V-belt, snap ring and/or stud bolt through fixed block (fixing device).
The discharging scroll of turbine shroud 3 comprises the first discharging scroll 1 and the second discharging scroll 2.The first discharging scroll 1 comprises the first exhaust outlet 1a.The upstream side that along turbine wheel 4 flow direction of waste gas of waste gas from the first exhaust outlet 1a towards turbine wheel 4 is positioned at upstream side partly is blown, that is, and and output.The second discharging scroll 2 comprises the second exhaust outlet 2a.The part that along waste gas flow direction turbine wheel 4 be positioned at the downstream side of first exhaust outlet 1a of waste gas from the second exhaust outlet 2a towards turbine wheel 4 is blown, that is, and and output.
The outmost edge that radially is positioned at of each blade 4b is called as leading edge RE, and the downstream side axial edge that the flow direction along waste gas of blade 4b is positioned at the downstream side is called as trailing edge TE.The peripheral edge between leading edge RE and trailing edge TE of blade 4b is called as shroud edge SE.
The part of the covering shroud edge SE of the inwall of turbine shroud 3 is called as guard shield wall SW.
The tubular wall that guard shield wall SW is configured to have the horn mouth shape is directed to trailing edge TE with the waste gas that will be fed in the gap between two adjacent blade 4b.Guard shield wall SW is configured to have arc guard shield wall SW1 and the cylindrical shroud wall SW2 that links together.
Arc guard shield wall SW1 be cover turbine blade 4b flow to the changeover portion wall surface of (arcuate segment of shroud edge SE will be called as curved edge hereinafter), flowing to the changeover portion place, the flow direction of waste gas becomes axial direction from radial direction.The cross section of arc guard shield wall SW1 has and the corresponding to arcuate shape of the shape of curved edge.
Cylindrical shroud wall SW2 is the wall surface that covers turbine blade 4b along the flow direction of waste gas in the downstream side of arc guard shield wall SW1.Cylindrical shroud wall SW2 is configured to the cylinder form parallel substantially with axial direction.
The first exhaust outlet 1a of the first discharging scroll 1 is an annular exit, and waste gas is exported towards leading edge RE from the radial outside of turbine blade 4b through the first exhaust outlet 1a.The runner towards leading edge RE direct exhaust of the first exhaust outlet 1a (opening part) is along extending with the vertical substantially direction of axial direction, shown in Figure 1B.
Shown in Figure 1A and Figure 1B, the second exhaust outlet 2a of the second discharging scroll 2 locates to offer at arc guard shield wall SW1 (curved bending section in the cross section of guard shield wall SW).
Particularly, the second exhaust outlet 2a is an annular exit, and waste gas is exported towards curved edge (flow direction of waste gas becomes the section of axial direction from radial direction at blade 4b) from the radial outside of turbine blade 4b through the second exhaust outlet 2a.The runner towards the curved edge direct exhaust of the second exhaust outlet 2a (opening part) extends along the direction that tilts with respect to axial direction, shown in Figure 1B.In this case, the second exhaust outlet 2a tilts with respect to axial direction, thereby between the axial direction of the axis of the second exhaust outlet 2a and turbine wheel 4, limits arc angle.
Isolated partition wall 10 at the first discharging scroll 1 and the second discharging scroll 2 is arranged in the inside of turbine shroud 3.
As shown in Figure 3, partition wall 10 extends to the exhaust gas entrance 3a (near the zone of the part that is connected to discharge manifold) of turbine shroud 3.The upstream side part that the flow direction along waste gas of the first discharging scroll 1 is positioned at upstream side is communicated with exhaust gas entrance 3a all the time.
As shown in Figure 3, the part that the flow direction along waste gas of discharge passage is positioned at the upstream side of the first discharging scroll 1 is limited partition wall 10, thereby has the section area that successively decreases that reduces towards the downstream side.
Transfiguration intercommunicating pore 11 is formed in the part of this restriction portion of formation (choked section) of partition wall 10, between the first discharging scroll 1 and the second discharging scroll 2, to be communicated with.Transfiguration intercommunicating pore 11 is opened through variable volume valve 9 or closes.
Control unit of engine (ECU) is carried out the opening/closing control operation and the aperture control operation of variable volume valve 9 through the electric actuator (not shown).When the aperture through variable volume valve 9 control transfiguration intercommunicating pores 11, the amount of waste gas that is directed to turbine blade 4b from the second discharging scroll 2 is controlled.
As shown in Figure 3, exhaust gas bypass intercommunicating pore 13 is formed in the outer wall of the second discharging scroll 2, so that (silencing apparatus one side) guides a part of waste gas towards the downstream side through walking around turbine blade 4b.Exhaust gas bypass intercommunicating pore 13 is opened through exhaust gas by-pass valve 12 or closes.
ECU carries out the opening/closing control operation and the aperture control operation of exhaust gas by-pass valve 12 through the electric actuator (not shown).When the aperture through exhaust gas by-pass valve 12 control exhaust gas bypass intercommunicating pores 13, the amount of waste gas of walking around turbine blade 4b is controlled.
For example, driving with the slow-speed of revolution under the situation of motor, ECU close variable volume valve 9 and exhaust gas by-pass valve 12 both, make all waste gas all only through the first discharging scroll 1.Secondly, the rotating speed at motor increases so that under the situation that the flow of waste gas increases, the aperture of ECU control variable volume valve 9 makes all waste gas through the first discharging scroll 1 and the second discharging scroll 2.Rotating speed at motor further increases so that under the situation that the flow of waste gas increases, ECU opens exhaust gas by-pass valve 12, walks around the flow of the waste gas of turbine blade 4b with control.
When the aperture of the aperture of controlling variable volume valve 9 based on the operating mode of motor in the above described manner and exhaust gas by-pass valve 12, can suitably control the pressure of waste gas and the boost pressure of turbosupercharger, thereby can improve the fuel consumption of motor.
Now, with the advantage of describing first embodiment.
The first exhaust outlet 1a is arranged on the position near the leading edge RE of turbine blade 4b, thereby is directed into the leading edge RE of turbine blade 4b from the waste gas of first exhaust outlet 1a output.
By contrast, the second exhaust outlet 2a is formed among the arc guard shield wall SW1.Therefore, when opening variable volume valve 9, be directed into the curved edge of the shroud edge SE of blade 4b from the waste gas of second exhaust outlet 2a output.
Shown in Figure 1B, when the second exhaust outlet 2a is formed among the arc guard shield wall SW1, can make from the waste gas of first exhaust outlet 1a output and from the angle (intersection angle) of converging between the waste gas of second exhaust outlet 2a output to diminish.Therefore, can be limited or minimize by generation from the caused turbulent flow of collision between the waste gas of first exhaust outlet 1a output and the waste gas of exporting from the second exhaust outlet 2a.Like this, can be limited in and produce the waste gas turbulent flow in the inside of turbine wheel 4, the generation of waste gas turbulent flow in the inside of turbine wheel 4 is minimized.
In addition, be arranged in the upstream side part that flows to changeover portion (flow direction of waste gas becomes the section of axial direction at turbine wheel 4 from radial direction) from the position of converging that the waste gas of first exhaust outlet 1a output and waste gas from second exhaust outlet 2a output merge together.Therefore, in the inside of turbine wheel 4 waste gas that converges is adjusted through flowing to changeover portion, afterwards, from the adjusted waste gas of turbine wheel 4 outputs.Therefore, limited in the outlet port of turbine wheel 4 generation waste gas turbulent flow.
As stated, first embodiment's turbosupercharger can be limited in the inside of turbine wheel 4 and the outlet place turbulization of turbine wheel 4.Therefore, the compared with techniques with formerly proposing can improve turbine efficiency (turbine efficiency under the state that variable volume valve 9 is opened particularly).
In addition, because turbine efficiency is enhanced, therefore, can improve moment of torsion through the boost pressure that increases turbosupercharger.The improvement of the improvement of fuel consumption and turbo (turbo lag) has realized the raising of vehicle drive performance.
(second embodiment)
To the second embodiment of the present invention be described with reference to Fig. 4.Among the embodiment below, will indicate by identical label with the assembly that the assembly of in first embodiment, discussing is similar.
In a second embodiment, be arranged in the downstream side part (right portions of the inwall of the second exhaust outlet 2a of Fig. 4) in downstream side with the flow direction of waste gas in the turbine wheel 4 that the vertical substantially vertical wall 21 in downstream side of axial direction is formed on the inwall of the second exhaust outlet 2a.The vertical wall 21 in downstream side preferably extends along circumferential direction around whole turbine shroud 3.Yet, the invention is not restricted to this, therefore, the vertical wall 21 in downstream side can only partly extend on circumferential direction along turbine shroud 3.
Owing to be provided with the vertical wall 21 in downstream side, therefore, can further reduce in turbine wheel 4 from the waste gas of first exhaust outlet 1a output and from the angle of converging between the waste gas of second exhaust outlet 2a output.Like this, can further limit or minimize, and therefore can further improve turbine efficiency by the caused waste gas turbulent flow of the collision of waste gas in the inside of turbine wheel 4.
In addition, even under the situation crooked owing to the exhaust flow of exporting from the first exhaust outlet 1a from the exhaust flow of second exhaust outlet 2a output, the vertical wall 21 in downstream side also can limit from the flow of the waste gas of second exhaust outlet 2a output and reduce.
Therefore, can increase, thereby can improve turbine output from the flow of the waste gas of second exhaust outlet 2a output.In addition, owing to can limit the generation of waste gas turbulent flow, therefore can improve turbine efficiency.
(the 3rd embodiment)
To the third embodiment of the present invention be described with reference to Fig. 5.
In the 3rd embodiment, be arranged in the upstream side part (left part of the inwall of the second exhaust outlet 2a of Fig. 5) of upstream side with the flow direction of waste gas in the turbine wheel 4 that the vertical substantially vertical wall 22 of upstream side of axial direction is formed on the inwall of the second exhaust outlet 2a.The vertical wall 22 of upstream side preferably extends along circumferential direction around whole turbine shroud 3.Yet, the invention is not restricted to this, therefore, the vertical wall 22 of upstream side can only partly extend on circumferential direction along turbine shroud 3.
Particularly, in the 3rd embodiment, the vertical wall 21 in downstream side all is arranged on the second exhaust outlet 2a place with the vertical wall 22 of upstream side.
Owing to be provided with the vertical wall 22 of upstream side, therefore, can further reduce in turbine wheel 4 from the waste gas of first exhaust outlet 1a output and from the angle of converging between the waste gas of second exhaust outlet 2a output.Like this, can further limit or minimize by the caused waste gas turbulent flow of the collision of waste gas, and can further improve turbine efficiency.
The separation that can limit owing to the waste gas of exporting from the first exhaust outlet 1a in addition, causes the inside of the second exhaust outlet 2a, producing eddy flow.
Therefore, can limit owing to eddy flow the exhaust flow from second exhaust outlet 2a output is produced interference, and therefore can further improve turbine efficiency.
(the 4th embodiment)
To the fourth embodiment of the present invention be described with reference to Fig. 6.
In the 4th embodiment; The downstream side part (right part of Fig. 6) that the flow direction of waste gas in the turbine wheel 4 that R part 23 (the arc turning is connected to guard shield wall SW and has arc section, make the segmental arc of arc section at guard shield wall SW tangential contact arc turning) is formed in the open end of the second exhaust outlet 2a is arranged in the downstream side is connected with guard shield wall SW smoothly.R part 23 is preferably extended along circumferential direction around whole turbine shroud 3.Yet, the invention is not restricted to this, therefore, R part 23 can only partly be extended on circumferential direction along turbine shroud 3.
Since be provided with R part (arc turning) 23, therefore, can be mobile reposefully from the waste gas of second exhaust outlet 2a output along guard shield wall SW.Particularly, can limit the exhaust flow of exporting from the second exhaust outlet 2a separates with guard shield wall SW.
Therefore, can be limited in from what the waste gas of first exhaust outlet 1a output and waste gas from second exhaust outlet 2a output merged together and converge the exhaust flow turbulization of converging the position, and therefore can improve turbine efficiency.
(the 5th embodiment)
To the fifth embodiment of the present invention be described with reference to Fig. 7.
The 5th embodiment is second embodiment and the 4th embodiment's combination.
Particularly, in the 5th embodiment, the vertical wall 21 in downstream side is formed on the second exhaust outlet 2a place, and R part (arc turning) 23 is formed on the attachment portion (turning) that the vertical wall 21 in downstream side is connected to guard shield wall SW and locates.
Like this, can realize second embodiment's advantage and the 4th embodiment's advantage simultaneously.Particularly, can further be limited in from what the waste gas of first exhaust outlet 1a output and waste gas from second exhaust outlet 2a output merged together and converge the waste gas turbulization of converging the position.Therefore, can further improve turbine efficiency.
(the 6th embodiment)
To the sixth embodiment of the present invention be described with reference to Fig. 8.
In the 6th embodiment, the present invention is applied to the tilting turbine that leading edge RE tilts with respect to axial direction.
Here, describe with reference to Fig. 8, in Fig. 8, the 4th embodiment is bonded in the tilting turbine (the downstream side part that the flow direction of waste gas in the turbine wheel 4 that R part 23 is formed on the open end of the second exhaust outlet 2a is arranged in the downstream side).Yet, the invention is not restricted to this combination.That is, any embodiment in the foregoing description all can combine with the tilting turbine.
Under the present invention and situation that the tilting turbine combines, can further reduce the angle of converging between the first exhaust outlet 1a and the second exhaust outlet 2a, and therefore can further improve the turbine efficiency of tilting turbine.
Those skilled in the art will expect other advantages and modification easily.Therefore, in a broad aspect, the invention is not restricted to the detail, typical equipments and the illustrated examples that illustrate and describe.
Claims (4)
1. turbosupercharger that is used for explosive motor comprises:
Turbine shroud (3) comprises a plurality of discharging scrolls (1,2), and each in said a plurality of discharging scrolls (1,2) is suitable for producing eddy flow from the waste gas by explosive motor output, and is suitable for the eddy flow of waste gas is discharged into the inboard of turbine shroud (3);
Turbine wheel (4); Be suitable for through by said a plurality of discharging scrolls (1; 2) waste gas of supply rotation, wherein, said turbine wheel (4) is suitable for discharging by said a plurality of discharging scrolls (1 along the axial direction of turbine wheel (4); 2) waste gas of supplying along the radial direction of turbine wheel (4) from the radial outside of turbine wheel (4), wherein:
Said a plurality of discharging scrolls (1,2) comprising:
The first discharging scroll (1) comprises first exhaust outlet (1a), and waste gas is partly exported towards the upstream side that the flow direction along the middle waste gas of turbine wheel (4) of turbine wheel (4) is positioned at upstream side through first exhaust outlet (1a);
The second discharging scroll (2) comprises second exhaust outlet (2a), and waste gas is exported through second exhaust outlet (2a) is positioned at the downstream side of first exhaust outlet (1a) towards the flow direction along waste gas of turbine wheel (4) part,
Said turbine shroud (3) comprises the guard shield wall (SW) of the shroud edge (SE) that covers turbine wheel (4),
Said guard shield wall (SW) comprises the arc guard shield wall (SW1) that flows to changeover portion that has arc section and be arranged in turbine wheel (4), and flowing in the changeover portion of turbine wheel (4), the flow direction of waste gas becomes axial direction from radial direction in turbine wheel (4),
Second exhaust outlet (2a) is offered in arc guard shield wall (SW1).
2. turbosupercharger according to claim 1; It is characterized in that, be formed on the downstream side part of inwall that in the turbine wheel (4) flow direction of waste gas is arranged in second exhaust outlet (2a) in downstream side with the vertical substantially vertical wall in downstream side (21) of axial direction.
3. turbosupercharger according to claim 1 and 2; It is characterized in that, be formed on the upstream side part of inwall that in the turbine wheel (4) flow direction of waste gas is arranged in second exhaust outlet (2a) of upstream side with the vertical substantially vertical wall of upstream side (22) of axial direction.
4. turbosupercharger according to claim 1 and 2; It is characterized in that, be formed on the downstream side part of open end that in the turbine wheel (4) flow direction of waste gas is arranged in second exhaust outlet (2a) in downstream side with arc turning (23) that guard shield wall (SW) is connected smoothly.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011078610A JP5353938B2 (en) | 2011-03-31 | 2011-03-31 | Turbocharger |
| JP078610/2011 | 2011-03-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102733931A true CN102733931A (en) | 2012-10-17 |
| CN102733931B CN102733931B (en) | 2014-11-05 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210090855.9A Expired - Fee Related CN102733931B (en) | 2011-03-31 | 2012-03-30 | Turbocharger for internal combustion engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5353938B2 (en) |
| CN (1) | CN102733931B (en) |
| DE (1) | DE102012205198B4 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804861A (en) * | 2015-01-16 | 2016-07-27 | 福特环球技术公司 | Exhaust control valve branch communication and wastegate |
| CN110050116A (en) * | 2017-02-22 | 2019-07-23 | 株式会社Ihi | Booster |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB201322206D0 (en) | 2013-12-16 | 2014-01-29 | Cummins Ltd | Turbine housing |
| JP7395002B2 (en) * | 2020-08-04 | 2023-12-08 | 三菱重工エンジン＆ターボチャージャ株式会社 | turbine and turbocharger |
| WO2024095525A1 (en) * | 2022-11-02 | 2024-05-10 | 株式会社Ihi | Turbine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1508411A (en) * | 2002-12-13 | 2004-06-30 | 吴雄良 | Apparatus for controlling alternating drive of two power sources to vortex compressor and control method thereof |
| JP2007192125A (en) * | 2006-01-19 | 2007-08-02 | Toyota Motor Corp | Turbocharger |
| CN101368488A (en) * | 2007-08-06 | 2009-02-18 | 霍尼韦尔国际公司 | Variable-geometry turbocharger with asymmetric divided volute for engine exhaust gas pulse optimization |
| JP2010013972A (en) * | 2008-07-02 | 2010-01-21 | Toyota Motor Corp | Variable capacity type turbocharger |
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| JP2003035152A (en) * | 2001-07-25 | 2003-02-07 | Daido Steel Co Ltd | Turbocharger housing and method of manufacturing the same |
| DE10318737A1 (en) * | 2003-04-25 | 2004-11-25 | Daimlerchrysler Ag | Exhaust gas turbocharger has two part turbine housing with first and second channels, whereby first channel contains control grid with individually adjustable guide vanes, second has no vanes |
| US7269950B2 (en) | 2004-05-05 | 2007-09-18 | Precision Industries, Inc. | Staged turbocharger |
| JP2007023893A (en) | 2005-07-15 | 2007-02-01 | Toyota Motor Corp | Turbocharger |
| JP2007023894A (en) | 2005-07-15 | 2007-02-01 | Toyota Motor Corp | Turbocharger |
| JP2009281197A (en) * | 2008-05-20 | 2009-12-03 | Mitsubishi Heavy Ind Ltd | Mixed flow turbine |
-
2011
- 2011-03-31 JP JP2011078610A patent/JP5353938B2/en not_active Expired - Fee Related
-
2012
- 2012-03-30 CN CN201210090855.9A patent/CN102733931B/en not_active Expired - Fee Related
- 2012-03-30 DE DE102012205198.8A patent/DE102012205198B4/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1508411A (en) * | 2002-12-13 | 2004-06-30 | 吴雄良 | Apparatus for controlling alternating drive of two power sources to vortex compressor and control method thereof |
| JP2007192125A (en) * | 2006-01-19 | 2007-08-02 | Toyota Motor Corp | Turbocharger |
| CN101368488A (en) * | 2007-08-06 | 2009-02-18 | 霍尼韦尔国际公司 | Variable-geometry turbocharger with asymmetric divided volute for engine exhaust gas pulse optimization |
| JP2010013972A (en) * | 2008-07-02 | 2010-01-21 | Toyota Motor Corp | Variable capacity type turbocharger |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804861A (en) * | 2015-01-16 | 2016-07-27 | 福特环球技术公司 | Exhaust control valve branch communication and wastegate |
| CN105804861B (en) * | 2015-01-16 | 2019-11-19 | 福特环球技术公司 | Exhaust control valve branch communication and wastegate |
| CN110050116A (en) * | 2017-02-22 | 2019-07-23 | 株式会社Ihi | Booster |
| CN110050116B (en) * | 2017-02-22 | 2021-06-15 | 株式会社Ihi | Pressure booster |
| US11162375B2 (en) | 2017-02-22 | 2021-11-02 | Ihi Corporation | Turbocharger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102733931B (en) | 2014-11-05 |
| JP5353938B2 (en) | 2013-11-27 |
| JP2012211572A (en) | 2012-11-01 |
| DE102012205198B4 (en) | 2020-06-18 |
| DE102012205198A1 (en) | 2012-10-04 |
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