CN1100200C - Turbosupercharger for Internal combustion engine in vehicle - Google Patents
Turbosupercharger for Internal combustion engine in vehicle Download PDFInfo
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- CN1100200C CN1100200C CN99113851A CN99113851A CN1100200C CN 1100200 C CN1100200 C CN 1100200C CN 99113851 A CN99113851 A CN 99113851A CN 99113851 A CN99113851 A CN 99113851A CN 1100200 C CN1100200 C CN 1100200C
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Abstract
The present invention discloses a turbocharger for a supercharging internal combustion engine of a vehicle, which is formed by combining a small-sized radial flow or mixing flow type turbocharger in an ordinary conventional structure capable of satisfying the requirements for the low rotation speed operating condition torque characteristics of the internal combustion engine for a vehicle with an inlet pre-screwing device of an air compressor. The turbocharger adopts air inlet positive pre-screwing technology of the air compressor to control the supercharging pressure of high rotation speed operating conditions of the internal combustion engine for a vehicle, and the excess supercharging and the overspeed of the turbocharger are prevented. The pre-screwing pressure control has the advantages of mature technology, simple structure, high safety, reliability, long service life, low cost, direct pressure control, rapid response and good effect.
Description
The present invention relates to the interior turbosupercharger of boosting internal combustion engine technical field that automobile (car, Light-duty Vehicle, truck), tractor, farm machinery and engineering machinery are used.
The Vehicular internal combustion engine power condition changing is frequent, load variations is big, rotating speed using scope broadness (rated speed of car internal-combustion engine have up to 6000 rev/mins).The general power of Vehicle Turbocharged internal-combustion engine is little, air-mass flow is little, (its turbine is the radial-flow type or the mixed-flow impeller of steamboat footpath size and adopts the non-blade nozzle ring for small-sized runoff of adapted or combined flow turbine pressurized machine, be vaneless scroll, so that in the changes in flow rate scope of broadness, obtain higher turbine efficiency).
Internal-combustion engine is not pursued in the Vehicular internal combustion engine supercharging to be had when high rotating speed and tries one's best power output big, but produces bigger moment of torsion or bigger tractive force is provided when requiring the slow-speed of revolution, is beneficial to vehicle and starts rapidly, quickens and climbing under big load.The Vehicle Turbocharged internal-combustion engine is by external characteristics work, and Maximum Torque generally appears at 55～60% rated speed places.For this reason, when being Vehicle Turbocharged internal combustion (IC) Engine Design or apolegamy pressurized machine, general all select near the operating mode the speed at maximum torque to determine the size of suitable turbosupercharger flow passage component sufficiently high boost pressure and torque reserve are arranged to guarantee slow-speed of revolution operating mode as optimal match point.Yet, when near the high rotating speed operating mode of Vehicular internal combustion engine rated speed moved, can be very big because of the air-mass flow increase, the through-current capability of selected pressurized machine flow passage component size then dislikes too little, cause supercharger speed and boost pressure to increase severely, produce too high mechanical load (maximum outbreak pressure) or cause the petrol engine detonation.
Thereby in order to make the Vehicle Turbocharged internal-combustion engine not only have higher boost pressure to have bigger moment of torsion in slow-speed of revolution operating mode, but also want to make it the excessive and pressurized machine overspeed seriously phenomenon of supercharging that too high, the maximum detonation pressure of boost pressure transfinites near the rated speed operating mode, not occur, just must suitably control, make internal-combustion engine in certain speed range more than the rotating speed, keep boost pressure constant or be no more than predefined limits value boost pressure.So the turbosupercharger of Vehicle Turbocharged internal-combustion engine must have characteristic and the key problem in technology that constrain and this particular requirement of pressure control function has formed the turbosupercharger of Vehicular internal combustion engine when the high rotating speed operating mode of internal-combustion engine.
In the prior art, the control that the turbosupercharger of Vehicular internal combustion engine can adopt or to suppress the technological scheme of boost pressure as follows: the venting of (one) exhaust gas by-pass valve: the part waste gas when bleeding off the high rotating speed operating mode of internal-combustion engine, the combustion gas quantity that enters the turbine work done is reduced, cause turbine power to reduce, thereby the reduction supercharger speed reduces boost pressure.This scheme is the pressure control measure that the turbosupercharger of Vehicle Turbocharged internal-combustion engine now generally adopts.Its advantage is: simple, and technology maturation, safety, cost are low.Shortcoming is: venting has caused the waste of high-temperature fuel gas energy, makes the internal-combustion engine oil consumption rate of high rotating speed operating mode higher; The venting valve opens and closes in high-temperature fuel gas for a long time, yielding and carbon deposit and occur being not closed completely and move clamping stagnation or inefficacy; Be subjected to the restriction of bleed valve spring rate, the boost pressure Changing Pattern is difficult to modulate according to the torque characteristics needs.(2) the turbine nozzle ring blade angle is regulated: rotary nozzle blade (change setting angle of nozzle vane) allows the nozzle blade discharge area reduce, the energy that can change the internal-combustion engine combustion gas raises the pressure of turbine inlet combustion gas, the turbine output rate increases, supercharger speed rises, and the gas compressor boost pressure increases; Otherwise, regulate setting angle of nozzle vane and strengthen by the nozzle blade discharge area, the turbine inlet gaseous-pressure is descended, the turbine output rate reduces, and supercharger speed reduces relatively, and boost pressure reduces.Like this,, when rotating speed reduces, can reduce the nozzle ring discharge area, make the unlikely decline of boost pressure excessive in internal-combustion engine slow-speed of revolution operating mode; For the high rotating speed operating mode of internal-combustion engine, when rotating speed raises, can increase the nozzle ring discharge area, make the unlikely excessive lift-rising of boost pressure.Thereby, guaranteed that slow-speed of revolution operating mode has higher boost pressure and obtains satisfied torque characteristics; For high rotating speed operating mode, also limited the increase of boost pressure, it is unlikely that supercharging to occur excessive.The turbine nozzle ring blade angle is regulated because of realizing automatically controlled step-less adjustment and not have the energy dissipation that venting causes that its effect is better than the exhaust gas by-pass valve venting.The advantage of this technology is: under the condition that does not increase high rotating speed operating mode rate of fuel consumption, increase low speed torque; Enlarged the Operational Zone of low rate of fuel consumption; More and more higher engine exhaust and noise regulation law can meet the demands.Shortcoming is: complex structure, volume be big, cost an arm and a leg; The reliability of structure and operation system is relatively poor; The high-temperature fuel gas in space leaks turbine efficiency is reduced between nozzle vane and the turbine volute; The amplitude of accommodation that the nozzle vane angle changes is limited, and excessive adjustments can cause that the air-flow angle of attack and degree of reaction change the excessive turbine efficiency that causes and decline to a great extent.Because the turbocharger arrangement of Vehicular internal combustion engine is several all to be typical small-sized runoff of standard or combined flow turbine supercharger structure unlimitedly---adopt non-blade nozzle ring (vaneless scroll), do not have nozzle vane, also without vane diffuser.Therefore, they nearly all adopt exhaust gas by-pass valve air bleed technique pressure control.The high performance vehicle (as special vehicles such as some tank, battlebuses) of having only only a few to pursue limit index just can be disregarded the restriction that becomes local breakthrough energy price ratio, specially installs nozzle blade additional and implements the variable-angle adjusting.Above binomial prior art can be referring to Zhu Daxin work " turbosupercharging and turbosupercharger ", China Machine Press, Beijing, 1992, the 401～447 pages and Lu Jiaxiang write " Vehicular internal combustion engine supercharging ", China Machine Press, Beijing, the relevant commentary in 1993, the 60～88 pages.(3) the variable stator angle adjustment of compressor inlet: the guide vane angle of rotating the prerotator at the compressor inlet place that is contained in turbosupercharger, can change the entry spin of gas compressor, make wasted work, boost pressure, corresponding the changing of air inlet relative velocity size and Orientation of gas compressor, thereby cause the change of compressor efficiency, turbosupercharger and internal-combustion engine joint work duty parameter.● Japanese patent gazette spy opens the variable stator angle adjustment of the compressor inlet pressure control technology that a kind of turbosupercharger that is suitable for car combustion engine adopts of having announced for flat 11-82036 number.In this technology, the angular setting that is arranged on the variable-angle guide vane of compressor inlet is controlled by a regulator with rotation.This regulator is one, and the operating structure of its structure and exhaust gas bypass bleed valve is basic identical with the air control unit of boost pressure as independent variable, promptly is made up of diaphragm, film bar, rocking arm, Regulation spring etc.When engine starting, the setting angle of guide vane is arranged on and produces the negative a certain angle of air inlet and maintained by regulator of prewhirling.Along with the increase of rotating speed, boost pressure improves, and regulator orders about guide vane and rotates, and after internal-combustion engine rotational speed was higher than a certain rotating speed, the air-flow that flows out guide vane was prewhirled by bearing to prewhirl just to become.Like this, this technological scheme can be utilized the negative raising boost pressure of prewhirling of air inlet in internal-combustion engine slow-speed of revolution operating mode: and arrived high rotating speed operating mode, and then adopt air inlet just prewhirling and suppress the excessive lift-rising of boost pressure.Thereby realized adopting simple mechanism to obtain the effect of good boost pressure characteristic, safe operation in whole working speed scope.The advantage of this technological scheme is that method is simple, and is safe and reliable, long service life, and pressure control is direct, and high rotating speed operating mode is constrain effective; Shortcoming is structure still is subjected to the regulator spring rate than the variation of exhaust gas by-pass valve scheme complexity (because only a regulator is just the same with the bleed valve structure) and boost pressure restriction, is difficult to separate modulation.● British patent gazette GB 2172340A has announced a kind of large and medium-sized axial flow turbine pressurized machine and regulating method thereof with variable cross section turbine and variable cross section gas compressor adjusting labyrinth that the marine internal combustion engine supercharging is adopted that be suitable for.The totally three kinds of blade angles adjustings of turbine nozzle blade, compressor inlet water conservancy diversion blade and compressor blade diffuser vane in this pressurized machine, have been adopted, make the marine internal combustion engine that under certain rotating speed, moves, by to the adjusting of turbosupercharger control, the fuel consumption minimum when reaching the continuous Maximum Power Output of internal-combustion engine.Three kinds of blade angles are mainly used nozzle vane angle adjustment boost pressure in regulating; The angle adjustment principal security gas compressor of compressor inlet water conservancy diversion blade and vane diffuser blade is at the high efficient area stable operation.Because complex structure, expense costliness, bulky, this pressurized machine is not suitable for adopting at Vehicular internal combustion engine.● Chinese patent publication number CN1196772A has announced a kind of turbo charge system of the geometry-variable with driving-aid.It is a kind of turbo charge system that is applicable to that rotating speed and the big internal-combustion engine of loading range adopt.In this pressurization system, the match selection of turbosupercharger and internal-combustion engine is in the high rotating speed operating mode of internal-combustion engine.This supercharging coupling, excessive and the pressurized machine overspeed seriously phenomenon of supercharging that boost pressure transfinites can not occur in high rotating speed operating mode, but increase the problem of having brought slow-speed of revolution operating mode boost pressure to cross the acceleration difference of low and supercharger rotor inertia increase generation because of the through-flow size of pressurized machine.For this reason, this technological scheme adopts waste gas pilot valve or additionaling power source (driving-aid) to improve the boost pressure increase moment of torsion of slow-speed of revolution operating mode.The effect of waste gas pilot valve is that the I. C. engine exhaust that flows to two passages of turbine volute during with high rotating speed operating mode only allows it pass through a passage (another passage is closed) when slow-speed of revolution operating mode, the gaseous-pressure that enters spiral case is increased, the turbine output rate increases, supercharger speed rises, and boost pressure improves.The effect of driving-aid (motor, oil hydraulic motor, pneumatic motor etc.) is to the defeated power that adds of the rotating shaft of turbosupercharger, increase moment of torsion, raising supercharger speed and boost pressure in slow-speed of revolution operating mode.In this system, also adopted the guide vane angle regulator, so that make the air that enters compressor impeller produce positive and negative prewhirling at compressor inlet.Its effect is as follows: in the high rotating speed operating mode of internal-combustion engine, should rotate guide vane the negative air inlet of prewhirling is provided, the working area of gas compressor be moved, to obtain high efficiency to higher flow district; In slow-speed of revolution operating mode, then should provide the air inlet of just prewhirling, avoid occurring surge, and the maximal efficiency of gas compressor is moved on to the internal-combustion engine low-speed range, help coupling.So, it seems that comprehensively this pressurization system be to still can being fit to the internal-combustion engine of high rotating speed operating mode as main operating conditions, then be not suitable for but be applied in the Vehicular internal combustion engine that low-speed torque characteristic and acceleration are had high requirements.In addition, the turbosupercharger of Vehicular internal combustion engine, volume is very little, rotating speed is high, bearing adopts inner supporting structure, rotating shaft is very thin, so the driving-aid of motor type structure can't be installed in the minimum middle case that is full of lubricant oil again in space (bearing support).If adopt the high-tension lubrication oil spurts to be installed in Pierre in the rotating shaft of the middle case position problem that wheel (a kind of turbine impeller structure) also exists rotor inertia to increase of pausing, also to set up one in addition and overlap hydraulic pressure fuel feeding and control system thereof, more increased the complexity of structure.In addition, if internal-combustion engine is long working time in the low speed operating mode, the energy charge of driving-aid bears also and must consider.
The objective of the invention is to provides that a kind of structure is the simplest, cost is minimum, can satisfy boost pressure requirement, safe and reliable in full rotating speed operating mode scope, than adopting exhaust gas by-pass valve means of deflation pressure control performance and the better turbosupercharger of using effect for the Vehicle Turbocharged internal-combustion engine.
The technological scheme that the present invention adopts for achieving the above object is: to the small-sized runoff of normal conventional structure or a combined flow turbine pressurized machine that can satisfy institute's coupling internal-combustion engine slow-speed of revolution operating mode boost pressure characteristic needs, implement compressor air inlet machine adjustings of just prewhirling in high rotating speed operating mode, to suppress or the excessive pressurisation pressure of the high rotating speed operating mode appearance of controlling combustion engine.
Turbosupercharger among the present invention program is by the requirement design of the torque characteristics of internal-combustion engine slow-speed of revolution operating mode (or boost pressure is with characteristic of internal-combustion engine rotational speed variation) or selects for use.The used turbosupercharger of the flow passage component size of its turbine and gas compressor and exhaust gas by-pass valve bleed strategy is close, but also smaller.This is that the valve of bleed valve is closed always because of the slow-speed of revolution operating mode at the Vehicle Turbocharged internal-combustion engine.Therefore, in slow-speed of revolution operating mode, for band valve pressurized machine with not with the same pressurized machine of valve, their boost pressure variation characteristic and be identical to the machine performance index of joining of same internal-combustion engine.If band valve pressurized machine satisfied join the needs of internal-combustion engine slow-speed of revolution torque characteristics, then the present invention program's that the flow passage component size is close with it turbosupercharger should be able to satisfy the needs of this internal-combustion engine slow-speed of revolution torque characteristics too.In view of the compressor air inlet machine boost pressure that can make supercharger air compressor of just prewhirling reduces, and the flow passage component size that reduces booster turbine can make boost pressure improve, therefore when the present invention program adopts the changeless prerotator of pre-swing angle constrain, to be spun on the boost pressure reduction that slow-speed of revolution operating mode causes just in advance in order compensating, the flow passage component size of turbosupercharger suitably to be reduced again.The compressor air inlet machine of the foundation of the present invention pressure control principle of prewhirling is as follows:
So-called compressor air inlet machine is prewhirled, and is meant to flow into the preceding air-flow absolute velocity of gas compressor rotary blade import
In impeller rotation round speed
The component velocity of direction
(Fig. 1).When
With
During equidirectional, claiming should
For just prewhirling; Otherwise then claiming should
Prewhirl for negative.Prewhirl by prerotator (fluid director leaf grating or the spiral inlet duct) generation of compressor inlet.Fig. 1 shows compressor inlet and axial exducer blade angle variset is housed goes into the situation schematic representation that the interruption-forming difference is prewhirled at compressor impeller.The airspeed triangle at impeller inlet/outlet place that drawn among the figure, symbolic significance is as follows among the figure:
---impeller angular velocity of rotation vector, rad/sr
0---impeller eye root radius, mmr
1t---impeller eye top radius, mmr
1---impeller eye geometrical mean radius, mm
r
1={ (r
0 2+ r
1t 2)/2}
1/2r
2---impeller outlet radius, mmR
0---guide vane outlet root radius, mmR
1t---guide vane outlet top radius, mmR
1---guide vane outlet geometrical mean radius, mm
R
1={ (R
0 2+ R
1t 2)/2}
1/2U---peripheral velocity vector, m/s
U=ω * r=ω re
ue
u---the peripheral velocity unit vector,
e
u=ω * r/| ω * r|W---air-flow relative velocity vector, m/sC---air-flow absolute velocity vector, m/s
C=C
m+ C
u=W+uC
m---the meridian of air-flow absolute velocity is to component velocity vector, m/s
C
m=C
r+ C
zC
r---the radial velocity component vector of air-flow absolute velocity, m/sC
z---the axial component velocity vector of air-flow absolute velocity, m/sC
u---the air-flow absolute velocity is at component velocity vector of peripheral velocity direction, m/s θ---pre-swing angle, θ=Arctg (C
1u/ C
1m), (°) β
1---the relative fluid inlet angle of impeller eye air-flow, following subscript: 1---impeller eye, geometrical mean radius r
1The value of position.2---impeller outlet, radius r
2The value of position.According to the implication of above-mentioned symbol as can be known: just prewhirl C
1u＞0, θ＞0; Zero prewhirls (claim again not have and prewhirl) C
1u=0,
θ=0; Bear and prewhirl C
1u＜0, θ＜0.
According to turbomachine Euler equation, the blade of gas compressor rotation is to the rate of doing work---the rim horsepower of every kilogram-mass gas of the impeller of flowing through
h
th＝C
2nu
2-C
1uu
1，J/s
Consequent blower outlet gas stagnation pressure (boost pressure)
p
c *=P
a[1+ (k-1) (1+ β
L+ β
Df) η
* Ad(C
2uu
2-C
1uu
1)/kRT
a]
K/ (k-1), in the bar formula, p
a---environment atmospheric pressure, barT
a---ambient air temperature, KK---ratio of specific heat, k=C
P/ C
V, air k=1.4R---gas constant, air R=287.04 J/ (kg.K) β
L---air loss influence coefficient, β
L=0.01 β
Df---wheel dropping loss influence coefficient, β
Df=0.02-0.03 η
* Ab---gas compressor stagnation isentropic efficiency
As can be seen from the above equation, prewhirl by " influence a C
1uu
1" change of boost pressure value is worked.Positive and negative and the value size of prewhirling is very big to the variable effect of boost pressure, the same value of prewhirling C
1uAt high pressure-charging pressure working condition (u at this moment
1The value height) impact effect is more much bigger than low pressure charging pressure working condition, therefore prewhirls pressure control to the high rotating speed operating mode of Vehicular internal combustion engine particularly suitable.Difference is prewhirled to the influence of impeller eye velocity triangle, clearly is shown in Fig. 1, can be analyzed intuitively by figure and prewhirl to the impeller eye relative velocity
With relative fluid inlet angle β
1Influence.Conclusion is as follows: just prewhirling makes the power input to compressor power reduction, and boost pressure reduces, and flows into relative velocity and descends, and fluid inlet angle increases relatively; The effect of the negative generation of prewhirling is then just the opposite.No matter just prewhirling or negative prewhirl the value of prewhirling C
1uBig more, influence big more.According to the difference in functionality of prewhirling, can regulate and control targetedly the specific requirement of the performance of gas compressor (boost pressure, surging condition, obstruction operating mode, high efficient area range of flow, the operation of high efficiency operating mode keep) aspect.
The general geometric shapes that characterizes prerotator (inducer leaf grating or spiral inlet duct) with pre-swing angle θ produces the ability of prewhirling in compressor impeller import cross section, its definition is θ=Arctg (C
1u/ C
1m), the symbol implication is as shown in Figure 1 in the formula.When just prewhirling, θ be on the occasion of; During negative prewhirling, θ is a negative value.For same compressor air inlet machine mass flow rate (is C
1mBe worth identical), pre-swing angle θ is big more, the C that prewhirls that prerotator produces
1uAlso big more.Also promptly, the θ value is big more, and the amplitude that it changes boost pressure is also big more.
As previously mentioned, for a Vehicle Turbocharged internal-combustion engine, compare with a flow passage component size that is applicable near the pressurized machine of operating mode supercharging coupling this internal-combustion engine speed at maximum torque, flow passage component as the turbosupercharger that adopts is undersized, then can cause the boost pressure in the internal-combustion engine rotational speed whole speed range from low to high to increase excessive, and the flow passage component size is more little, and the increased pressure that causes is just big more.Therefore for high rotating speed operating mode is constrain, the value that the compressor air inlet machine that needs prerotator to append generation is just being prewhirled is also big more, also is that pre-swing angle θ value is just big more.But the θ value increases, and can make the also corresponding increase thereupon of value of the air-flow negative angle of attack that flows into compressor impeller, makes the decrease in efficiency of gas compressor.Thereby should not adopt the pre-swing angle of excessive θ value constrain, its rational use should not exceed the scope of 10 °≤θ≤60 °.On the other hand, turbosupercharger for same flow passage component size, when the rotating speed using scope of the internal-combustion engine of its coupling increases, can the too high phenomenon of boost pressure appear equally in the high rotating speed operating mode of the internal-combustion engine that has increased rotating speed, it is constrain also must to make prerotator strengthen pre-swing angle θ value, and the rotating speed increasing amount is big more, and adding of θ value is also big more in a large number, based on the same consideration of efficient aspect, the reasonable using scope of θ value also should be 10 °≤θ≤60 °.
In the practicality, the pre-changeless prerotator of swing angle has boundless application prospect, because its structure is the simplest, safe and reliable, the life-span is long, cost is minimum, can satisfy the needs of pressure control requirement after 10 °≤θ of the choose reasonable≤60 ° value substantially.
The pre-changeless prerotator of swing angle, because pre-swing angle θ can not regulate variation, so can not independently modulate on demand the boost pressure of the full rotating speed operating mode of internal-combustion engine, this is its deficiency.But to slow-speed of revolution operating mode can not adopt negative prewhirl to boost be not a noncompensable shortcoming because slow-speed of revolution operating mode flow is low and wheel speed is low, " an influence C prewhirls
1uu
1" value little, thereby very little to the contribution of boost pressure lift-rising, reduce turbine flow passage component size not as adopting, the effect that the exhaust pressure of increasing combustion engine (promptly changing exhaust energy) rises boost pressure is remarkable.
Adopt pre-swing angle θ to change the deficiency that adjustable prerotator can be eliminated the constant prerotator of fixing pre-swing angle θ, in the entire internal combustion engine speed range, boost pressure is independently modulated on demand, but still be it should be noted that the amplitude of boosting of slow-speed of revolution operating mode is limited.(even adopt the value that has strengthened negative pre-swing angle, the increasing degree of boost pressure is also still limited).In view of can producing big high incidence, excessive negative pre-swing angle reduces compressor efficiency, so the reasonable using scope of the pre-swing angle θ of the adjustable prerotator of pre-swing angle is-40 °≤θ≤60 °.Adopting the shortcoming of the adjustable prerotator of pre-swing angle is complex structure, and price is more expensive, and installing space is big.Consider the deficiency of pressure control mode of the regulator of Japanese kokai publication hei 11-82036 communique technological scheme, so should adopt controlling mechanism commonly used in the Fan Regulation in the present invention program.
The structural type of inducer cascade type prerotator has axial exducer and two kinds of fluid directors radially.The blade angle of these two kinds of fluid directors all has adjustable and fixes two kinds of forms.
Compare with bypass venting pressure control device, the pre-swing angle θ that the present invention the adopts prerotator pressure control device that immobilizes has following advantage: 1) technology maturation, method is simple.2) whole pressure control device is worked under room temperature environment, not influenced by gas high-temperature, and is safe and reliable, the life-span is long.3) cost is low.Simple in structure, also lower to the requirement of component material, manufacturing and installation aspect.4) regulation and control are quick.Directly the control boost pressure feeds back directly, and responsiveness is good.5) high rotating speed operating mode pressure control is effective.What the same angle value of inducer blade produced prewhirls to the change amplitude of power input to compressor or boost pressure, increases with the increase of internal-combustion engine rotational speed.
Below, with accompanying drawing technology contents of the present invention is narrated explanation in conjunction with the embodiments.Fig. 2 shows the turbocharger arrangement of the present invention with the pre-cyclone of variable pre-swing angle axial exducer leaf grating.The main constituent elements of prerotator part is: 1---rolling bearing, and 2---goniometer, 3---gear ring, 4---fan-shaped gear piece, 5---sleeve, 6---the fluid director blade.The fluid director leaf grating is made up of a plurality of guide vanes 6 that (number of blade is Z
p), the tailing axle of each blade passes sleeve 5 and is coupled to one with the fan-shaped gear piece 4 of a slice.When fan-shaped gear piece when sleeve axis rotates, also rotate with the fixed all-in-one-piece guide vane of gear piece.Each fan-shaped gear piece is common again to be meshed with a rotating gear ring 3, keeps consistent synchronously to guarantee that each gear piece rotates, thereby makes the corner of each guide vane when swing angle changes in advance all identical.For reducing the pivoting friction of gear ring, adopt rolling bearing 1, and the corner of goniometer 2 measurement gear rings has been installed.A slice in gear ring or the fan-shaped gear piece is linked by intermediate gear and automatically controlled straight-line displacement or angular displacement actuator, just can carry out the regulation and control of variable pre-swing angle.Automatically controlled straight-line displacement or angular displacement actuator can adopt stepper motor or DC servo motor.The geometrical mean radius of fluid director leaf grating outlet shown in Figure 2 is bigger than the geometrical mean radius in gas compressor impeller inlet cross section, and the two then equates structure shown in Figure 3.These two kinds of structures are all commonly used, and Fig. 2 structure is prewhirled effective, Fig. 3 compact structure.
Fig. 4 shows the structure installation diagram of the pre-cyclone of the changeless axial exducer leaf grating of pre-swing angle.The geometrical shape of fluid director leaf grating and the nozzle ring of axial flow turbine are closely similar, available fine casting method cast inblock, material aluminium.There is shown with outlet mean radius R
1Cylndrical surface parting guide-ring after be launched into the resulting plane cascade shape in plane again.Characterize the pre-swing angle Φ of geometry that whole fluid director leaf grating produces the ability of prewhirling just by this plane cascade two physical dimensions---width a of throat and pitch t are definite according to following formula:
Φ=90 °-Arcsin (a/t), (°) in the formula, t=2 π R
1/ Z
p, Zp---the lobe numbers of fluid director leaf grating.The conversion relation of how much pre-swing angle Φ of fluid director outlet and the pre-swing angle θ of compressor impeller inlet air flow is:
θ＝Arctg[(r
1t-r
0)/(R
1t-R
0)×tgΦ]，(°)
For each guide vane angle of Fig. 2 and variable pre-swing angle axial exducer leaf grating shown in Figure 3, the pre-swing angle Φ of the geometry of pairing whole fluid director leaf grating value all can be one by one according to fluid director leaf grating outlet mean radius R
1The size of the corresponding a that measures on the leaf grating unfolded drawing of cylndrical surface is calculated according to following formula.
Fig. 5 shows the radially sketch of the pre-cyclone of fluid director leaf grating of variable pre-swing angle.Automatically controlled or gas, hydraulic control straight-line displacement final controlling element 1 promote gear ring 2 and rotate, thereby make the fan arc gear piece on each guide vane tailing axle with the gear ring engagement rotate the change that causes the guide vane angle synchronously.
Fig. 6 shows the structure installation diagram of the pre-cyclone of pre-swing angle changeless radially fluid director leaf grating.Guide vane ring 3 and intake duct shell wall 1 and 2 usefulness bolted on connections back integral body together are nested on the aerostatic press suction tude and use the semicircle screw radially fixing.Fig. 7 shows the structural drawing of guide vane ring 3.For preventing under the effect of air-flow power, to rotate, between 1 and 3 with screw or dowel fixes.The same with the axial exducer leaf grating, the pre-swing angle of the geometry of fluid director leaf grating radially
Φ＝90°-Arcsin(a/t)，(°)
In the formula, t=2 π R
1/ Z
P1, Zp---guide ring lobe numbers,
R
1---the guide ring exit radius of blade.The conversion formula of pre-swing angle Φ of geometry and the pre-swing angle θ of air-flow is
θ＝Arctg[(r
1t-r
0)B×tgΦ]，(°)
In the formula, the blade axial height (Fig. 7) at B---guide ring exit radius of blade place.
Different with the axial exducer leaf grating is when the blade rotation angle of fluid director radially, and not only a changes, R
1Also change.
Claims (1)
1. turbosupercharger that the Vehicle Turbocharged internal-combustion engine is used, it is immobilized by a normal conventional design of mini runoff or combined flow turbine pressurized machine and pre-swing angle or the pre-cyclone of adjustable compressor inlet combines.It is characterized in that: it is 10 °≤θ≤60 ° that the pre-swing angle of the pre-changeless prerotator of swing angle θ is rationally selected with scope; The reasonable using scope of pre-swing angle that pre-swing angle θ can change the prerotator of adjusting is-40 °≤θ≤60 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN99113851A CN1100200C (en) | 1999-07-06 | 1999-07-06 | Turbosupercharger for Internal combustion engine in vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN99113851A CN1100200C (en) | 1999-07-06 | 1999-07-06 | Turbosupercharger for Internal combustion engine in vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1290806A CN1290806A (en) | 2001-04-11 |
| CN1100200C true CN1100200C (en) | 2003-01-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99113851A Expired - Fee Related CN1100200C (en) | 1999-07-06 | 1999-07-06 | Turbosupercharger for Internal combustion engine in vehicle |
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| Country | Link |
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| CN (1) | CN1100200C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102384107A (en) * | 2011-11-08 | 2012-03-21 | 奥凯嘉集团有限公司 | Lemniscate spiral air inlet supercharger |
| CN102705072B (en) * | 2006-07-17 | 2014-09-24 | 霍尼韦尔国际公司 | Method for calibrating a turbocharger |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2354560A1 (en) * | 2010-01-28 | 2011-08-10 | Siemens Aktiengesellschaft | Device for adjusting variable guide vanes |
| US9243550B2 (en) * | 2012-03-12 | 2016-01-26 | Ford Global Technologies, Llc | Turbocharger compressor inlet flow control |
| CN103899411A (en) * | 2014-03-04 | 2014-07-02 | 大同北方天力增压技术有限公司 | External rotation speed measuring device of supercharger |
| CN106761972B (en) * | 2016-12-22 | 2018-08-31 | 东方电气集团东方汽轮机有限公司 | A kind of axial admission radial direction exhaust casting volute structure |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56148619A (en) * | 1980-04-18 | 1981-11-18 | Hino Motors Ltd | Supercharger for motor car engine |
| GB2172340A (en) * | 1985-03-08 | 1986-09-17 | Hitachi Shipbuilding Eng Co | Turbocharger for diesel engine and method of controlling same |
| CN1196772A (en) * | 1995-07-28 | 1998-10-21 | 涡轮动力系统有限公司 | Motor-assisted variable geometry turbocyarging system |
| JPH1182036A (en) * | 1997-09-11 | 1999-03-26 | Hitachi Ltd | Exhaust turbo-charger |
-
1999
- 1999-07-06 CN CN99113851A patent/CN1100200C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56148619A (en) * | 1980-04-18 | 1981-11-18 | Hino Motors Ltd | Supercharger for motor car engine |
| GB2172340A (en) * | 1985-03-08 | 1986-09-17 | Hitachi Shipbuilding Eng Co | Turbocharger for diesel engine and method of controlling same |
| CN1196772A (en) * | 1995-07-28 | 1998-10-21 | 涡轮动力系统有限公司 | Motor-assisted variable geometry turbocyarging system |
| JPH1182036A (en) * | 1997-09-11 | 1999-03-26 | Hitachi Ltd | Exhaust turbo-charger |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102705072B (en) * | 2006-07-17 | 2014-09-24 | 霍尼韦尔国际公司 | Method for calibrating a turbocharger |
| CN102384107A (en) * | 2011-11-08 | 2012-03-21 | 奥凯嘉集团有限公司 | Lemniscate spiral air inlet supercharger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1290806A (en) | 2001-04-11 |
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