CN204646407U - Axial entrance, radial exit type pressurized machine - Google Patents

Axial entrance, radial exit type pressurized machine Download PDF

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Publication number
CN204646407U
CN204646407U CN201420825880.1U CN201420825880U CN204646407U CN 204646407 U CN204646407 U CN 204646407U CN 201420825880 U CN201420825880 U CN 201420825880U CN 204646407 U CN204646407 U CN 204646407U
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CN
China
Prior art keywords
return port
air
port
blade
inlet
Prior art date
Application number
CN201420825880.1U
Other languages
Chinese (zh)
Inventor
K·马哈拉特卡尔
M·G·斯瓦茨兰德尔
S·帕蒂尔
M·J·弗勒利希
G·库尔卡尼
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伊顿公司
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Priority to US201361897928P priority Critical
Priority to US61/897928 priority
Priority to US201461991166P priority
Priority to US61/991166 priority
Priority to US29/499,660 priority patent/USD816717S1/en
Priority to IN2337/DEL/2014 priority
Priority to US29/499660 priority
Priority to IN2337DE2014 priority
Application filed by 伊顿公司 filed Critical 伊顿公司
Application granted granted Critical
Publication of CN204646407U publication Critical patent/CN204646407U/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32Engines with pumps other than of reciprocating-piston type
    • F02B33/34Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/36Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type
    • F02B33/38Engines with pumps other than of reciprocating-piston type with rotary pumps of positive-displacement type of Roots type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32Engines with pumps other than of reciprocating-piston type
    • F02B33/34Engines with pumps other than of reciprocating-piston type with rotary pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/126Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/16Other safety measures for, or other control of, pumps
    • F02B2039/162Control of pump parameters to improve safety thereof
    • F02B2039/164Control of pump parameters to improve safety thereof the temperature of the pump, of the pump drive or the pumped fluid being limited
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04Cooling of air intake supply
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00Geometry
    • F04C2250/10Geometry of the inlet or outlet
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04Heating; Cooling; Heat insulation

Abstract

The utility model relates to a kind of axial entrance, radial exit type pressurized machine, and this axial entrance, radial exit type pressurized machine comprise tubular shell, and this tubular shell comprises the plane of inlet (IP) perpendicular to pelvic outlet plane (OP).Rotor mounting recess (1030,1020) is arranged in the internal surface of the entry wall (1063) being parallel to plane of inlet.Triangular-shaped outlet (104) is in pelvic outlet plane.Entrance (101) is in plane of inlet.At least two axial flow return port (1222) are in plane of inlet (IP).Or pressurized machine comprises inlet axis (IA).The rotor of each band blade comprises the spin axis parallel with inlet axis (IA), wherein when the rotor rotates, each blade sequentially engages along inlet axis (IA), wherein each blade reverses along the length of their respective rotors, and these blades are set the time seals relative to outlet fluid for making entrance.At least two return port (122,1222) are in tubular shell.

Description

Axial entrance, radial exit type pressurized machine

Technical field

A kind of supercharger systems of the utility model relate generally to.More specifically, a kind ofly the supercharger systems of high-pressure ratio and low outlet temperature is obtained by making cooling-air be back to pressurized machine from intercooler.

Background technique

Pressurized machine can be embodied as to combustion engine supply pressurized air.When air is compressed, so more air can be supplied, make vehicle can produce more power.There is various different pressurized machine to use, comprise wave formula, roots-type, double-screw type and centrifugal.Their difference is that air is compressed and air moves to the mode of engine intake manifold.

Roots type super charger is positive-displacement pump, and it forces air around the periphery of rotor and air is blown into manifold.Therefore, Roots type super charger is referred to as " blower " sometimes.More particularly, Roots type super charger has the lobed rotor of two counter-rotatings.Along with rotor rotates, it will be pushed against housing towards outlet/exhaust port and enter engine intake manifold in the space of air capture between rotor by two rotors.By making air move into manifold with the speed higher than the speed of motor consumed cabin air, set up pressure.

Because it simply designs, Roots type super charger is used widely.But Roots type super charger has some shortcomings.When the chamber of the air that is captured opens wide engine intake manifold, according to thermomechanics and fluid mechanics principle, the forced air reverse flow in engine intake manifold is in pressurized machine.In addition, the air leakage caused by gap may be there is between rotor, or the leakage caused by the gap between rotor blade and housing, described gap provides for thermal expansion tolerance.The reverse movement of air and air leakage all cause the low efficiency of roots-type supercharging.Further, because it produces the person's character of high discharge temperature, it can detract engine performance.Such as, when the temperature of discharging air raises, it can cause the pinking of motor, excessive wear or cause thermal damage.

In many positive discharge capacity compression sets such as reciprocal compressor, increase pressure by the volume reducing to be occupied by gas.Such as, piston by the gas compression of large volume be for physically more small volume to increase pressure.But in roots-type device, the mechanism not as piston carrys out pressurized gas.Root's blower draws air from low pressure suction side and makes this air move on to high-pressure outlet side.When the low-pressure air drawn by Roots type super charger and high-pressure outlet side contacts, so there is backflow action, thus pressurized gas from outlet return to pressurized machine in and by the gas of low-pressure gas boil down to more high pressure.Therefore, the gas compression in pressurized machine is occurred by this backflow action.According to thermodynamic principle, this is also heated to higher temperature by by the low-pressure gas compressed.After gas compression, pressurized air is expressed into high-pressure outlet side from pressurized machine by the blade of Roots type super charger.

Usually, Roots type super charger by outlet port can the high-pressure air of heat be used for the action that refluxes.But, can by use after intercooler can relatively cold pressurized gas cool Roots Compressor.But, determine to obtain as pressurized machine provides minimum operating temperature, provides backflow notch size, layout and geometrical shape needed for the best of most high workload efficiency backflow action to be still problem simultaneously.

Model utility content

In order to improve supercharging, by the pressure ratio term being exactly motor, need high-pressure ratio.Pressure ratio represent pressurized machine before the compression carried out of absolute air pressure and pressurized machine after the ratio of absolute air pressure.Under higher pressure ratio or supercharging, larger air quality is fed to motor, thus allows more substantial fuel combustion, also obtains higher power stage.

In one embodiment, a kind of axial entrance, radial exit type pressurized machine comprise tubular shell.This tubular shell comprises plane of inlet (IP) and pelvic outlet plane (OP).Plane of inlet is perpendicular to pelvic outlet plane.Rotor mounting recess (1030,1020) is arranged in the internal surface of the entry wall (1063) being parallel to plane of inlet.Triangular-shaped outlet (104) is in pelvic outlet plane.Entrance (101) is in plane of inlet.At least two axial flow return port (1222) are in plane of inlet (IP).

Advantageously, each in described at least two axial flow return port is notch, and this notch has the profile matched with the sections on involute.

Advantageously, described pelvic outlet plane (OP) also comprises at least two runoff return port (122).

Advantageously, each in each and described at least two runoff return port in described at least two axial flow return port has four sides and these four sides are the one in the notch of circular arc, rectangular notch, oval pore or circular port.

Advantageously, described pressurized machine also comprises header board (1060), and this header board is separated with described entry wall (1063) by adjustment distance (TD).

Advantageously, described pressurized machine also comprises the passage (1061) in described header board (1060), and described passage aligns with each in described at least two axial flow return port (1222).

Advantageously, described pressurized machine also comprises the base plate (1071) between described entry wall (1063) and described header board (1060), and described base plate makes described entrance (101) fluidly separate with described at least two axial flow return port (1222).

Advantageously, described pressurized machine is also included in the supporting portion (1010) in described entrance (101), and described base plate (1071) is abutted against in described supporting portion.

Advantageously, the return port area A that occupies in described tubular shell of described axial flow return port portdetermined by following formula:

Wherein, P 1inlet pressure, P 2the pressure maximum ratio of described outlet, T 1inlet temperature, T 2be outlet temperature, R is gas constant, N rPMbe the maximum (top) speed of the rotor in pressurized machine, unit is rev/min, V transferVolumebe transmitted volume of air, α refers to and determines inlet temperature T 1under the velocity of sound, γ be wait hold wait pressure ratio of specific heat.

Advantageously, the desirable port area A that occupies of described axial flow return port iPortat A portthe scope of to 4/4th times in.

Advantageously, described desirable port area A iPorta porthalf to 2 times.

Advantageously, described desirable port area A iPorta port2/3rds.

Advantageously, described pressurized machine is also included at least two runoff return port (122) in described pelvic outlet plane (OP), described return port area A portthe area that described in also comprising, at least two runoff return port occupy.

Advantageously, described pressurized machine is also included at least two runoff return port (122) in described pelvic outlet plane (OP), wherein said desirable port area A iPortalso occupied by described runoff return port (122).

In another embodiment, a kind of axial entrance, radial exit type pressurized machine comprise tubular shell, and this tubular shell comprises plane of inlet (IP) and pelvic outlet plane (OP).Plane of inlet is perpendicular to pelvic outlet plane.Rotor mounting recess (1030,1020) is arranged in the internal surface of the entry wall (1063) being parallel to plane of inlet.Inlet axis (IA) is placed in the middle between rotor mounting recess.Triangular-shaped outlet (104) is in pelvic outlet plane.Entrance (101) is in plane of inlet.Rotor (102,103) with blade all comprises the spin axis parallel with inlet axis (IA) separately.When the rotor rotates, blade sequentially engages along inlet axis (IA).Each blade reverses along the length of their respective rotors.It is that (being in time, are timed to) makes entrance seal relative to outlet fluid by setting that these blades are set the time.At least two return port (122,1222) are in tubular shell.

Advantageously, described at least two return port are the axial flow return port (1222) in described plane of inlet (IP).

Advantageously, described at least two return port are the runoff return port (122) in described pelvic outlet plane (OP).

Advantageously, described at least two return port are the axial flow return port (1222) in described plane of inlet (IP), and described pressurized machine also comprises at least two runoff return port (122) in described pelvic outlet plane (OP).

Advantageously, the return port area A that occupies in described tubular shell of described at least two return port portdetermined by following formula:

Wherein, P 1inlet pressure, P 2the pressure maximum ratio of described outlet, T 1inlet temperature, T 2be outlet temperature, R is gas constant, N rPMbe the maximum (top) speed of the rotor in pressurized machine, unit is rev/min, V transferVolumebe transmitted volume of air, α refers to and determines inlet temperature T 1under the velocity of sound, γ be wait hold wait pressure ratio of specific heat.

Advantageously, the desirable port area A that occupies of described at least two return port iPortat A portthe scope of to 4/4th times in.

Advantageously, described desirable port area A iPorta porthalf to 2 times.

Advantageously, described desirable port area A iPorta port2/3rds.

Advantageously, each in described at least two axial flow return port is notch, and this notch has the profile matched with the sections on involute.

Advantageously, each in each and described at least two runoff return port in described at least two axial flow return port has four sides and these four sides are the one in the notch of circular arc, rectangular notch, oval pore or circular port.

Advantageously, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree completes air inlet phase, blade rotary 20-50 degree is to complete stop phase place, blade rotary 20-40 degree completes sealing phase place, blade rotary 25-50 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.

Advantageously, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree is to complete air inlet phase, blade rotary 0-50 degree is to complete stop phase place, blade rotary 15-70 degree is to complete sealing phase place, blade rotary 20-70 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.

Advantageously, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree is to complete air inlet phase, blade rotary 20-50 degree is to complete stop phase place, blade rotary 10-50 degree is to complete sealing phase place, blade rotary 20-80 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.

Advantageously, each in described at least two return port is configured as to be opened at 10 to 15 degree of blade rotary.

Advantageously, each in described at least two return port is configured as to be opened at 30 to 40 degree of blade rotary.

Advantageously, stopped by respective vanes completely when described at least two return port are sized to before blade rotary to the corresponding port in described at least two return port.

Advantageously, each blade has profile, and each in described at least two return port is configured as the sections of described blade profile.

Advantageously, described pressurized machine also comprises header board (1060), and this header board is separated with described entry wall (1063) by adjustment distance (TD).

Advantageously, described pressurized machine also comprises the base plate (1071) between described entry wall (1063) and described header board (1060), and described base plate makes described entrance (101) fluidly separate with described at least two return port (1222).

Advantageously, described pressurized machine also comprises the passage (1061) in described header board (1060), and described passage aligns with each in described at least two return port (1222).

Advantageously, described pressurized machine also comprises the recycling pipe (112) being connected to described passage (1061).

Advantageously, described pressurized machine also comprises:

Intercooler, it includes an inlet and an outlet, described intercooler connect into from the outlet of described pressurized machine receive by the air that blows and connect into cooling and discharge the air that receives as return air; With

Conduit, the return port of pressurized machine described in described tubes connection and the outlet of described intercooler to receive described return air,

Wherein, the rotor of described band blade comprises rotatable the first rotor and rotatable second rotor,

Wherein, each in described the first rotor and the second rotor comprises at least three blades,

Wherein, between each adjacent blades, be formed with corresponding space,

Wherein, when space is aligned, described return port is orientated the cooling-air provided to adjacent space from described intercooler,

Wherein, when providing cooling-air to described adjacent space, described adjacent space is sealed relative to described entrance and described outlet.

Advantageously, described the first rotor at least comprises the first blade and the second blade, described second rotor at least comprises Three-blade and quaterfoil, described at least two return port comprise the first return port and the second return port, when return air is exposed to described second return port and the space between described Three-blade and described quaterfoil, described first return port is by described first runner sealing, and when described return air is exposed to described first return port and the Second gap between described first blade and described second blade, described second return port is sealed by described quaterfoil.

Advantageously, described pressurized machine has the thermoae limit of 150 degrees Celsius and the outlet pressure of 4.4:1 and the pressure ratio of inlet pressure.

Advantageously, each blade reverses 60-130 degree along the length of their respective rotors.

The method controlling supercharger systems comprises a use pressurized machine pumped air, and this pressurized machine comprises entrance, outlet and return port.The air of institute's pumping can cool and discharged to combustion engine in intercooler.Computing device can receive and process the sensor signal of sensor.The sensor signal received can to determine the aperture of the valve in return-flow catheter compared with predetermined value, and return-flow catheter is connected to and the air of discharge is transferred to return port from intercooler.Further, compare according to this, can the aperture of modulating valve.

It should be understood that general introduction above and detailed description are subsequently only exemplary and explanat, instead of the restriction to model utility required for protection.

Accompanying drawing explanation

To be incorporated in this specification and the accompanying drawing forming this specification part is used for interpretation work principle exemplified with several embodiment together with illustration.

Figure 1A is the schematic diagram of the supercharger systems with cooling-air return-flow catheter.

Figure 1B is with cooling-air return-flow catheter and has the schematic diagram of the supercharger systems of air by-pass conduit.

Fig. 1 C is the schematic diagram with the air return of combination and the supercharger systems of air by-pass conduit.

Fig. 2 A-2C is the example of control system.

Fig. 3 is the chart that pressure ratio is shown.

Fig. 4 A is the analog result of the temperature distribution that the pressurized machine not having cooling-air to reflux is shown.

Fig. 4 B is the analog result of temperature distribution of the pressurized machine shown with cooling-air backflow.

Fig. 5 is an example of Roots type super charger.

Fig. 6 A-6D is each view of pressurized machine main casing.

Fig. 7 is the view of alternative pressurized machine main casing.

Fig. 8 is the view of the transfer of air between blade.

Fig. 9 is the alternative view of the transfer of air between blade.

Figure 10 is the comparison of the phase diagram of blade timing.

Embodiment

Present general is in detail with reference to illustrative embodiments of the present utility model, and its example illustrates in the accompanying drawings.As possible, in all figure, the identical reference character of use is referred to same or analogous part.Thick arrow line shows air-flow direction, unless otherwise mentioned.

Figure 1A illustrates supercharger systems 10, and it is for the exit condition by controlling pressurized machine 100 to the adjustment of return air.Pressurized machine 100 can have air inlet 101, chamber 105 and outlet 104.Supercharger systems 10 is backflow control system, for controlling backflow action to regulate the temperature at outlet 104 place of pressurized machine 100.Pressurized machine 100 is positive discharge capacity air pumps, and can be roots-type or dissimilar, such as screw type.When blow on one's own initiative or pumped air time, along with air is by chamber 105, pressurized machine 100 heats this air.Pressurized machine 100 is for compressing the air and the power stage increasing motor of going to combustion engine.Make the outlet air return of high pressure in low voltage control volume owing to transferring to outlet along with the low voltage control volume of air, therefore compress.System 10 comprises outlet air for importing cooling and non-thermal outlet air and for the mechanism of the action that refluxes.

During backflow, the importing of cooling-air increases the pressure ratio of pressurized machine compared to the method for prior art.Pressure ratio characterizes the pressurized machine supercharging amount that can provide to motor, and the ratio of hydrodynamic pressure after hydrodynamic pressure before being pressurized machine and pressurized machine.Gas such as ambient air is the preferably fluid for compressing, but, sometimes, due to exhaust gas recirculatioon (EGR), other fluid a certain amount of may be there is, as exhaust.

At present, the pressure ratio of Roots type super charger is by the maximum operation temperature of auto levelizer or the restriction of thermoae limit.Thermoae limit is decided by the thermal expansion of such as oil degradation, metal parts (such as rotor and/or housing), the factors such as tired and endurance issues of running.By being reduced in the temperature of the fluid circulated in pressurized machine, the pressure ratio of device can increase, within remaining on the thermoae limit of device simultaneously.

Usually, in order to reduce the temperature of the air going to motor, use intercooler cool from the air of pressurized machine.The reduction of air temperature will increase air density, and therefore this improve the ability that motor produces more high-power and torque.By making cooling-air be back to pressurized machine from intercooler, the pressure ratio of pressurized machine increases, and reduces the temperature of the discharge air carrying out automatic pressure intensifier 100 simultaneously.

In figure ia, air inlet 101 allows ambient air to enter pressurized machine 100.Air inlet 101 is positioned on tubular shell, in the plane of inlet IP of the inlet side of pressurized machine 100.Chamber 105 can hold two rotors 102,103.Each rotor rotates around the axis being parallel to first axle or inlet axis IA.Each rotor can have at least two blades, but is preferably three or four.Rotor 102 has three blades 102A, 102B and 102C.Similarly, rotor 103 has three blades 103A, 103B and 103C.These blades can be parallel or reverse.For the example reversing design, rotor can be high screw type or master screw type.High spiral is 120 ° of rotors, and master screw is 60 ° of rotors.Each angle represents the torsional capacity of rotor in length.Also can use other windup-degree according to design, exemplary slew range is 60-130 degree.

Such as, Figure 10 compares the phase diagram of two kinds of exemplary boost devices and the first example of port timing and the second example.On the right, pressurized machine has the three blade rotors of the 5th generation GEN V-type that two are manufactured by Eaton company.Blade reverses 60 degree along their length.The phase diagram of example 1 shows the rotating distance of each blade of rotor.Specify blade to carry out 210 degree of rotations to complete air inlet (entering) phase place, suck air at this by entrance 1011 or 1012.Then blade advances 50 degree to complete stop phase place, and advances 40 degree to complete sealing phase place.Backflow action has been assigned with the vane travels of 40 degree, and discharge or vane travels that exhaust phase place has been assigned with 200 degree with by Air blowing pressurized machine.By return port 122 and 1222 being designed to be less than distributed vane travels, transmit the backflow action that volume energy experience is unexpected and permanent.Such as, 10 to 15 degree that axial flow backflow notch 1222 can be designed to rotate at rotor are opened, and obtain permanent cooling-air backflow action thus.

The example 2 of Figure 10 uses the pressurized machine with two four-lobe rotor.Blade reverses 160 degree along their length.The air inlet phase time is increased to 280 degree, discharges phase time and is increased to 220 degree.Stop phase place and reduce to 20 degree, sealing phase time reduces to 10 degree.Backflow is increased to 80 degree actuation time.If axial flow return port 1222 is still opened as above in 10 to 15 degree of blade rotary, then cooling-air backflow action extends in time further.Such as, if use larger axial flow return port, full circle port, so port can not throw open for whole backflow phase place or keep standard-sized sheet.When circular port, if its size is set as the full cut-off by blade blockage, so it can utilize the 30-40 degree of blade rotary to open this circular port completely.

Table 1 summarize for the twist blade Gen V manufactured by Eaton company (the 5th generation) and TVS (two eddy current series) pressurized machine can exemplary timing range.For appointment blade phase place, give total timing range and compare with six kinds of other timing schemes of exemplary boost device.

table 1

In order to throwing open and closing of return port can be realized, advantageously make port be configured as and be similar to blade shape.Therefore, forward Fig. 8 to, upper axial flow return port 1222 is depicted as aligns with blade 102A.Because port is the external curve roughly to mate blade of " beans " shape, so port can not suffer in air leakage to exit volume 140E or transmit in volume 140S.On the contrary, blade can stop that cooling-air transmission gets back to inlet volumetric 140I with the air sealing up side leakages.Although allow cooling-air to leak into exit volume 140E, wish the extruding of the outlet air that restricted passage return port is returned.The leakage that " beans " shape prevents axial entrance return port 1222 and exports between 104 can be utilized.This design can be utilized to be back to limit cooling-air the backflow volume 140B specified in designated phase, as shown in Figure 9.Therefore, axial flow return port 122 is the notches being designed to have the profile matched with the sections on involute.This notch can have the rounded edges for smooth-going air flow profile.The notch of " beans shape " can be described to the notch with four sides, and each side is circular camber line.Alternatively, axial flow return port 1222 is rectangular notch, oval pore or circular port, and its size is set as opening completely in 30 to 40 degree of blade rotary, and size is set as being blocked completely by blade when blade mating holes.

Rotor 102,103 can be mutually the same.Or blade 102A, 102B, 102C of rotor 102 can reverse clockwise, and blade 103A, 103B, 103C of rotor 103 can reverse counterclockwise.For Figure 1A, 5 and the example of 8-10, because rotor 102,103 has the blade of torsion, therefore pressurized machine 100 can have much better air-treatment characteristic.In addition, pressurized machine 100 can produce less air impulsive motion and turbulent flow.The length of rotor 102,103 can change.The size of pressurized machine 100 can be determined by the length of rotor 102,103.Along with rotor 102,103 rotates, these rotors can mesh together along first axle, inlet axis IA, and these rotors can rotate along the engagement of contrary direction.

Between the adjacent blades that the air entering the chamber 105 of pressurized machine 100 can be trapped in rotor 102 (such as, between blade 102A and 102B) space in.Between the adjacent blades that air also can be trapped in rotor 103 (such as, between blade 103A and 103B) space in.The air be captured can be transferred into outlet 104 to discharge from pressurized machine 100.In the example shown, pressurized machine is axial entrance, radial export-oriented pressurized machine.This means that intake air advances in tubular shell along the rotor axis being parallel to inlet axis IA.Along with rotor rotates, air leaves inlet axis IA diametrically and moves towards outlet 104, and this outlet is perpendicular in the pelvic outlet plane OP of outlet axes OA.Inlet axis IA is vertical with outlet axes OA.Outlet 104 can be leg-of-mutton with the shape of mating rotor 102,103, or other shape allowing air easily to leave.Because transmit air volume can be greater than the discharge capacity of motor 120, therefore the air pressure in motor 120 can increase.In other words, Roots type super charger 100 is by producing boost pressure by increasing air buildup to intake manifold.

Intercooler 110 can comprise entry port 113, go out port one 11 and recycling pipe 112.Each rotor 102,103 can have attached recycling pipe 112, is sent back to pressurized machine in a balanced fashion to make cooling-air.The outlet 104 that entry port 113 can be connected to pressurized machine 100 discharges air to receive.Intercooler 110 can be any mechanical device being used as radiator.In addition, intercooler 110 can comprise bar, plate core and fin (not shown).Once the discharge air carrying out automatic pressure intensifier 100 enters intercooler 110, air just can move by bar and plate core and advance to port one 11 of going out, and is turned cold by heat trnasfer simultaneously.The general details of the working mechanism of intercooler is known, therefore will not be described herein.The size of intercooler 110, shape and design can the notable changes according to the performance of supercharger systems and spatial requirement.Intercooler 110 can be air-air formula or Air-Water formula.

Go out port one 11 by the intake manifold 121 of cooling-air discharged to motor, and port one 11 of going out is connected to conduit 112 by optional valve 114A and valve sensor and actuator 114.Conduit 112 can outwards the left side of outbound port 111, right side or both sides branch be out.The other end of conduit 112 is connected to the runoff return port 122 of pressurized machine 100, thus cooling-air can be transmitted between the blade of rotor.The embodiment substituted may realize conduit separately with the connection of axial flow return port 1222 or the connection that combines together with runoff return port 122.

Some supercharger systems utilize return port to reduce from pressurized machine noise out.As the substituting of outlet air return receiving heat, can use runoff return port 122 receive from the cooling-air of conduit 112.This can reduce the noise coming from pressurized machine work.Therefore, there is conduit 112 and can improve the noise of pressurized machine, vibration and uneven compliance (NVH) ability.

The size of the runoff shown in adjustment figure and axial flow return port 122,1222, shape and position may be needed, to provide best cool air input to pressurized machine.The cool air runoff return port 122 of Fig. 5 is positioned on main casing 106 after entrance 101 and before outlet 104.That is, runoff return port 122 is different from entrance 101 and outlet 104.Align in space between runoff return port 122 energy and the blade of rotor, make along with rotor rotation, when space is through runoff return port 122, cooling-air mixes with the air inlet in space.In order to ensure appropriate mixing, the distance between entrance and runoff return port is greater than the distance between space and its adjacent reflow port.As shown in Figure 5, runoff return port can from outlet than from entrance more close to.

The size and shape of runoff and axial flow return port 122,1222 is also set as that cooling for reflux air imports between rotor by the position forming " sealed volume " at rotor.That is, rotor rotates to make air move to outlet from the entrance of pressurized machine, and there is a position, and the space between this position blade is all sealed from entrance and exit.By strategic layout and the shape of runoff and axial flow return port 122,1222, cooling for reflux air is directed in this space or sealed volume.

Such as, two runoff return port 122 can be used, as shown in Figure 5, or one can be used, as shown in Fig. 6 A-9.Runoff return port 122 can be rectilinear or circular arc, as shown, or can be other adjustable shape, such as avette or circular.Preferably, the shape of port allows throwing open and closing of port, thus backflow action is occurred suddenly with very high speed.

Inlet side axial flow return port 1222 is by being positioned at inlet side and being positioned at the axial flow making cooling-air be promoted the high pressure reflow air through cooling by the position of drawing to the outlet side of high pressure, high temperature from the inlet side of the lower pressure of pressurized machine, lower temperature.Return air is along inlet axis IA at the track at inlet side axial flow return port 1222 place, and therefore, the cooling-air of high pressure along rotor length torrent, as shown in the thick arrow in Fig. 9.Therefore, inlet side axial flow return port 1222 supplements the axial entrance of pressurized machine, radial exit design.

Only can use inlet side axial flow return port 1222, only use outlet side runoff return port 122 or perform cooling-air by inlet side axial flow return port 1222 with the combination of outlet side runoff return port 122 and reflux.Therefore, the quantity of return port can change to six from two, and when two, each rotor has a port, and when six, each rotor has three ports.If port does less, then it can be the port that greater number implemented by each rotor.

As shown in Fig. 6 A-7, runoff return port 122 can be reduced to two from four in outlet 104 side of main casing 106.Axial flow return port 1222 is added in entry wall 1063 in entrance 101 side of main casing.In main casing 106, the inner side of entry wall 1063 comprises rotor mounting recess 1020 and 1030 in the plane being parallel to plane of inlet IP.In other replacement scheme, main casing is made up of axial flow return port 1222, and does not comprise any runoff return port 122.

Tubular main body 106 comprises header board 1060.In fig. 6, header board 1060 comprises machining path 10 61 to obtain the processing path leading to axial flow return port 1222.Path 10 61 receives connector to seal header board 1060 after machining.Alternatively, recycling pipe 112 is connected to path 10 61 and has the reflection of less air wave to promote axial return air to flow.For the ease of tubes connection, passage can be other shape except shown " mushroom " shape, such as circular, avette, rectangle or square.Fig. 7 eliminates path 10 61 to be conducive to being formed the header board 1060 of sealing.

Adjustment distance TD between entry wall 1063 and header board 1060 is selected to and allows return air be connected to axial flow return port 1222 and can not form air toward the excessive standing wave got back to outside chamber 105 or reflection.Adjustment distance TD is selected to restriction flow losses and the air throttle controlled in axial flow return port 1222.The additional control of flowing is determined by the length of the recycling pipe 112 between intercooler and refluxing chamber 1075 and diameter.Refluxing chamber 1075 can comprise the volume of air being exposed to runoff return port 122 and the volume of air being exposed to axial flow return port 1222.At least one separating part 1062 cooperates with the wall 1064,1065 of tubular shell and cooperates to form refluxing chamber 1075 with header board 1060.

Entrance 101 comprises supporting portion 1010 alternatively.As mentioned above, entrance 101 supplies air inlet or bypath air to the rotor 102,103 of pressurized machine.Supporting portion 1010 is in figure 6 c for the entrance region 1011 distributing to rotor 103 provides instruction with the entrance region 1012 distributing to rotor 102.Entrance 101 can be described as and extend a certain amount of of tubular shell.But, also advantageously, for each rotor limits entrance, make entrance region 1012 have entrance span, theta distributing in the border circular areas of rotor 102 of entry wall 1063 i.Use this convenient benchmark, inlet face is divided into 360 degree by the mid point around rotor mounting recess 1020.Sealing span, theta soccupy another part of entry wall 1063.Axial flow return port 1222 occupies backflow span, theta b, and the remaining part of border circular areas is used for rotor stroke to be adapted to discharge phase place and rotor engagement.The mirror image of each angular span is applicable to rotor mounting recess 1030.

Entrance 101 seals via the backflow volume in base plate 1071 and integrated manifold 1070 and opens.This base plate can be insert seal part or the part of shell casting.Supporting portion 1010 is connected to the base plate 1071 of integrated manifold 1070.Base plate 1071 is between entry wall 1063 and header board 1060 and form integrated manifold 1070 synergistically with the extension part of wall 1064 and 1065.Base plate 1071 by providing physical separation and making entrance 101 fluidly be separated with axial flow return port 1222 between entrance 101 with integrated manifold 1070.Therefore intake air can not mix with cooling for reflux air.

Entrance 101 runs through header board 1060 and to extend and crossing with plane of inlet IP along entry wall 1063.Axial flow return port 1222 is also in plane of inlet IP.Plane of inlet IP is perpendicular to inlet axis IA, and inlet axis IA is shown as from the page Fig. 6 C out.

Outlet 104 and when deployed runoff return port 122 are perpendicular in the pelvic outlet plane OP of plane of inlet IP.Pelvic outlet plane is also parallel to inlet axis IA.Outlet axes is shown as from the page Fig. 6 B out.Outlet axes perpendicular to inlet axis IA and perpendicular to pelvic outlet plane OP, as shown in Figure 6A.When to describe pressurized machine be axial entrance, radial outlet device, explain easily and be, air moves into turbocharger inlet 101 and vertically or along being parallel to the rotor axis of inlet axis IA by axial flow return port 1222.When pressurized machine works to intake air and return air, air is directed into and radially leaves outlet 104 relative to rotor axis, this means air along or be roughly parallel to outlet axes OA and discharge.This makes this pressurized machine be different from radial entrance, radial outlet device, and these devices do not have identical air-flow character or leak constraint.

The header board 1060 of main casing 106 separates with entry wall 1063 by adjustment distance TD.Adjustment distance TD is selected to the flowing regulating the return air through cooling to axial flow return port 1222.The aliging of integrated manifold 1070 and axial flow return port 1222 is selected to draws airflow guiding and enters chamber 105 along the direction exporting 104.By guiding flowing, compared to runoff return port 122, pressurized machine work obtains less with by Air blowing, because when rotor time rotational in chamber 105, air flows in the axial direction along rotor.

Use the example of Fig. 8 and 9, the return air through cooling leaves intercooler 110 and is drawn towards refluxing chamber 1075.Blade 102A-102D and 103A-103D reverses along the length of their respective rotors and is hollow, as indicated by hollow portion 102H and 103H.See Fig. 8, blade 102B and 102C is exposed to entrance 101 and allows the air of inlet volumetric 140I to enter main casing 105.Blade 102D seals near main casing 105.Blade 102A also seals near main casing 106 and stops its attached axial flow return port 1222 and stop its attached runoff return port 122.The transmission volume 140S of sealing is formed between blade 102A and 102D.The exit volume 140E of air is exposed to outlet 104 between blade 102A and 102B.

When rotor 102 rotates again, as shown in Figure 9, blade 102A no longer block axis flow back to flow port 1222 and no longer stop runoff return port 122.Return air through cooling can enter the space between blade 102A and 102D now.Although not requirement, ideally, transmit volume and still seal with entrance and exit and opens, mixed with the return air through cooling by the air of the transmission volume 140S sealed and formed to reflux and transmit volume 140B.Along with intake air moves on to outlet from entrance, intake air is heated.Return air through cooling follows thermodynamic principle, shifts to high temperature and shifts to low pressure from high pressure, be forwarded to outlet 104 thus from the entry end of rotor 102 from low temperature.As a result, pressurized machine blows out more substantial air between blade 102A and 102D.

When the rotor 102,103 in Fig. 8 and 9 engage and counter-rotating time, the timing of rotor makes rotor 103 be exposed to the input of cooling for reflux air in the time being different from rotor 102.So when rotor 102 block axis flows back to flow port 1222, rotor 103 makes the space between blade 103A and 103B be exposed to cooling for reflux air and transmits volume 141B to form backflow.When rotor 102 fully exposes its axial flow return port 1222, rotor 103 stops its axial flow return port 1222.The degree stopped or expose determines by the shape of blade 102A-102D, 103A-103D and size and by the shape of axial flow and runoff return port 122 and 1222, position and size.

As shown in Figure 8, the shape of blade 102A-102D, 103A-103D and the shape of orientation and axial flow and runoff return port 122 and 1222 and orientation are complimentary to one another.This complementary pairing allows the adjustment of sealing and timing.Therefore, along with blade is through return port, sealing is transmitted volume and is transmitted volume communication at difference and backflow.As above, axial flow or runoff return port use each other or do not use allows to carry out additional adjustment to the compression ratio of reflux characteristic and pressurized machine thus.

Therefore, in order to the compression ratio demand of client, system can be designed to desirable rotor speed operation pressurized machine to obtain desirable compression ratio, and the size of blade, orientation and timing are selected to the use of the one or both in supplementary axial flow and runoff return port to adapt to the realization of target compression ratio further.The larger control of the standing wave in chamber 105 is achieved.The larger control of outlet pulsation is achieved.

As the annex point of air stream customization regulation and control, the length of input 104 and diameter are selected to the length of the standing wave affected in chamber 105.Therefore, not only the adjustment distance TD of integrated manifold 1075 is controlled, and the length of input 104 is also controlled.

Outlet 104 and refluxing chamber 1075 separate by least one separating part 1062.Outlet 104 can match with the pipeline making air be communicated with intercooler unit with separating part 1062.Further, separating part 1062 and refluxing chamber 1075 can match with recycling pipe 112.

The go out width of port one 11 of intercooler can be considered the size of specific pressurized machine, type and space, be designed to meet the needs of specific pressurized machine together with other performance requirement.Such as, the go out width of width energy specific run off return port 122 of port one 11 is much wide.As an example, when the width of the single return-flow catheter 112 used is for 8mm, the width of port one 11 of going out can be 43mm.In other design, runoff and/or axial flow return port and attached conduit can have than port one 11 and the large cross-section area of attachment tube thereof of going out.Port and conduit are of a size of application-specific and adjust to guarantee from supercharger outlet to intercooler, to the fluid stream of return port.Therefore, the law of thermodynamics of pressure and temperature affects return port position and size, makes the cooling-air leaving intercooler 110 be back to pressurized machine 100 by conduit 112.

As an example, the size of runoff and axial flow return port 122,1222 is by port area A portfollowing estimation formula determine:

Wherein, P 1inlet pressure, P 2the pressure maximum ratio of outlet, T 1inlet temperature, T 2be outlet temperature, R is gas constant, N rPMbe the maximum (top) speed of pressurized machine, unit is rev/min (" RPM "), V transferVolumebe transmitted volume of air, α refers to and determines inlet temperature T 1under the velocity of sound, γ be wait hold wait pressure ratio of specific heat.

Port area A portdetermine that shoulding be cooling for reflux transfer of air distributes the great gross area.Therefore, the area summation distributing to axial flow return port 1222 and/or runoff return port 122 should reach port area A port.Desirable port area A iPortat A portthe scope of 1/4th (1/4) to 4 times in.More specifically, desirable port area A iPortfor A port1/2nd (1/2) to 2 times.More specifically, desirable port area A iPorta port2/3rds (2/3).

Because axial flow return port 1222 impels axial air flow towards outlet 104, therefore advantageously, distribution end open area A portwhole or most of give these return port.Therefore, consider positive limit, axial flow return port 1222 should comprise feasible port area A large as far as possible porteven if support to omit runoff return port 122.But, if need other area to meet port area A port, meet the blade rotary of above-mentioned 10-15 degree to 30-40 degree for opening axial flow return port 1222 simultaneously, so just should area outside allocation to runoff return port 122.When requiring king-sized port area, can need to comprise multiple runoff return port 122, as shown in Figure 5.When the constraint that physically inlet area is installed, axial flow return port 1222 must be omitted to be conducive to only adopting runoff return port 122.Therefore, one or more groups return port can be had to meet design constraints.Distribute one or more return port and perform the cooling of backflow volume 140B, prevent air leakage from getting back to entrance simultaneously, reduce from the extruding of outlet 104 as far as possible and preferably allow throwing open and closing of return port.

For example, do not have the pressurized machine of runoff return port 122 for only having axial flow return port 1222, the transmission volume 140S that the return air through cooling enters by sealing transmits volume 140B to form backflow.The cooling for reflux volume of air of low-pressure inlet air and higher pressure seals and opens by integrated manifold 1075.Cooling for reflux air parallel is in rotor and enter axial flow return port 1222 along the direction that air is discharged in outlet 104.The blade of rotor 102 and 103 is configured to prevent inlet volumetric 140I, 141I and backflow from transmitting " short circuit " between volume 140B, 141B as in Fig. 8 and 9.That is, cooling for reflux air can not communicate with entrance 101, because blade is sealed in case backflow air arrives entrance 101.As described in, wish that there is transmission volume 140S, the 141S by sealing, its not before cooling-air backflow with entrance 101 or export 104 and communicate.Although backflow may be allowed to transmit volume 140B be communicated with some between outlet space 140E, 141E, in this illustration, entrance, backflow and outlet air volume are independent of one another.The Sealing period of 15-45 degree is provided.The backflow angle of 20-50 degree is also provided.The rotor also applying 60-130 degree reverses.

Except the width of runoff and axial flow return port 122,1222, the length of return-flow catheter 112 can also be regulated with the backflow of adjustment to pressurized machine.The position of runoff and/or axial flow return port is selected to and is ejected in pressurized machine cooling-air to cool air mass.Spray in the sealed volume between rotation blade that the ideal position of air is rotor.That is, injected air mass and entrance and exit seal are opened by the position at rotor place.In order to customize cooling effect, the air quantity retracting eddy pressurizer blade must be controlled.By selecting length and the width of return port, adjustable is injected in the air between the blade of pressurized machine, adjusts flowing thus.By controlling the amount of flowing, such as, by valve (as described below), obtain other adjustment.

By making cooling-air reflux and mix mutually with the air input of pressurized machine 100, air will be deposited in intake manifold 121 more closely.Pressure ratio is by higher than the accumulation of the air do not mixed with cooling-air.In other words, by using the high pressure cool air from the outlet 111 of intercooler, the temperature of pressurized machine 100 inside can reduce.Therefore, higher pressure ratio can be obtained.Therefore, the size that need not increase pressurized machine 100 just can provide larger supercharging to motor 120.

In addition, because cooling-air mixes with the air in pressurized machine, therefore export from pressurized machine the air obtained and can more cool, therefore improve combustion efficiency.Meanwhile, low temperature can allow pressurized machine 100 to reach higher pressure ratio before reaching the thermoae limit of pressurized machine.In addition, because the air entering pressurized machine 100 is mixed with the comparatively cool air refluxed by conduit 112, therefore pressurized machine 100 can suck the air hotter than common pressurized machine.In other words, the supercharger systems through retrofiting can improve the ability of pressurized machine process high temperature air inlet.

Such as, strategically can reduce tolerance, come from because cooling for reflux air prevents pressurized machine from reaching the high heat that air inlet blows.Or higher intake temperature can adapt to usual tolerance, because cooling-air will make integrated air temperature in normal operating range.Because the relation between thermal expansion tolerance and outlet temperature is linear, if therefore outlet temperature reduces, the tolerance so between rotor can reduce, and the tolerance between rotor with housing can reduce the percentage the same with the reduction of outlet temperature.

In supercharger systems 10, use recycling pipe 112 can have other advantage.In the system of this remodeling, EGR (exhaust gas recirculatioon) Processing capacity can be improved, because can be cooled by return air by the air of EGR recirculation.

Conduit 112 also can improve the efficiency of pressurized machine 100.There is the temperature that conduit 112 can reduce outlet 104, and and then the bulk temperature operating range of reduction pressurized machine 100.If reduce bulk temperature operating range, the tolerance so between rotor and housing can become tight, and therefore improves the working efficiency of pressurized machine 100.

The layout of runoff and axial flow return port 122,1222 away from entrance 101 and can export 104, and close to rotor 102,103.The size and shape of runoff and axial flow return port 122,1222 is designed to the flowing of optimization cooling-air between intercooler to rotor blade, reduces the use as the port of air outlet slit simultaneously as far as possible.By selecting the size (length, width, highly) of conduit 112, and utilize high-pressure air to the movement of low pressure area, cooling-air is retracted to hot cell 105.

Figure 1B is with cooling-air return-flow catheter 112 and has the schematic diagram of the supercharger systems 11 of air by-pass conduit 115C.System 11 allows air not need to be bypassed around during the full capacity of pressurized machine at combustion engine.So, require limited engine booster or do not require engine booster period in, air can get around from motor 120 and get back to the entrance 101 of pressurized machine 100.After by-pass conduit 115C is shown in intercooler 110, but other position is also possible.Bypass valve 115A is controlled by bypass actuator 115.Except actuating mechanism and electronic controller, bypass actuator 115 can also comprise sensor and open or close parameter to receive instruction and to send signal for control bypass valve.

Fig. 1 C is the schematic diagram with the air return of combination and the supercharger systems 12 of by-pass conduit.Multi-way valve 116A receives the cooling-air from intercooler outlet 111 by combined catheter 116B.Except actuating mechanism and electronic controller, actuator 116 can also comprise sensor and open or close parameter to receive instruction and to send signal for control multi-way valve 116A.Multi-way valve 116A can be controlled so as to make air in by-pass conduit 115C around the entrance 101 to pressurized machine 100.Multi-way valve 116A also bootable cooling-air arrives runoff return port 122 by conduit 112.Although multi-way valve 116A is depicted as single valve, advantageously, more than one valve can be used or is branched off into the additional conduits realizing bypass and backflow principle.

Figure 1B and 1C provides the control of backflow action and can regulate the temperature at outlet 104 place of pressurized machine 100 and flow.That is, bypass valve 115A or multi-way valve 116A can be controlled so as to adjust charge flow rate by adjusting the air being supplied to entrance 101.Backflow action is adjusted by control valve 114A or multi-way valve 116A.Although illustrate only runoff return port 122 in Figures IA-1 C, as mentioned above, some combinations of axial flow return port 1222, multiple runoff return port 122 or axial flow and runoff return port only can be had.

Fig. 2 A illustrates the control mechanism 20 of the backflow control system for Figure 1A.Control mechanism 20 can be programmed to control backflow action thus the temperature at outlet 104 place of adjustment pressurized machine 100.Control mechanism 20 can by the method regulating return air to implement the exit condition for controlling pressurized machine 100.

Control mechanism 20 can control the air circulation by system 10, thus allows a part of cooling-air to be back to pressurized machine 100.Sometimes, stop backflow may be favourable, therefore by controlling the actuator 114 being attached to valve 114A, the amount of cooling-air can be adjusted to maximum flow from zero by control mechanism 20 always.Calculate according to engine airflow demand and temperature requirements and control the maximum flow of backflow, and therefore can according to operating conditions and because of vehicle different different and different with driver.

Whether control mechanism 20 can control to carry out refluxing or bypass action.When blow air is to motor on one's own initiative for pressurized machine, control mechanism 20 control valve 114A and 116A is to provide backflow action.But when not needing cooling, or when pressurized machine dallies, control mechanism controls bypass valve 115A and valve 114A or valve 116A with the inlet side making air rap around to pressurized machine.If air is cooled by intercooler 110, so bypath air can cooling of charge device and flow through passive (non-blow) air of system.Because always do not need this passive cooling, so so that uncolled air is rapped around in system before bypass valve 115A being connected to intercooler 110.

Control mechanism 20 can be a part for the control mechanism used in vehicle, other treatment device many-sided perhaps of such as car-mounted computer, computing chip and control vehicle operation.Control mechanism comprises usual computing element, such as, send and receiving port, processor, storage and programming.

Control mechanism 20 can be a part of control unit of engine (ECU).Control mechanism 20 can comprise the actuator 114 of controller 150, sensor 151,152,153 and operating valve 114A.Actuator 114 can comprise sensor, for collecting the data of the aperture about valve 114A.Quantity and the layout of sensor can change according to implemented feedback control, and therefore system can have the sensor more more or less than described example and actuator.Sensor can be various types of, and it can detected state and transmission signal, such as temperature, pressure, speed or air mass flow (speed).Described sensor can comprise polytype, and therefore sensor can measure various states, such as temperature and air mass flow.

The mode of operation being suitable for vehicle is opened or closed valve 114A energy is as determined in controller 150.The aperture of valve 114A can change to full cut-off from standard-sized sheet.

The opening/closing of valve 114A can be determined by the temperature in the air temperature at measurement outlet 104 place or motor 120.In addition, the decision of the aperture of open/closed valve 114A or modulating valve 114A also can be affected from the temperature reading of the air of port one 11 discharge of going out.

Sensor 151 can be mass air flow sensor (MAF), measures the mass flow rate in motor 120.Such as, sensor 151 can be hot wire sensor.Sensor 151 can be placed in motor 120.The reading of sensor 151 guarantees the optimum air amount being just fed into motor 120.Sensor 151 also can measure in-engine temperature.

Sensor 152 can be temperature transducer, measure leave the outlet 104 of pressurized machine 100 by the temperature of blow air.Sensor 152 also can measure the flow of air.The air blown out from pressurized machine 100 can need to be sufficiently cool before entering intake manifold 121.If air is not sufficiently cooled, so there will not be peak output active combustion process in motor 120.Therefore, air temperature can need to be reduced to reach optimum temperature by intercooler 110 thus the more high efficiency realized in motor 120 and more powerful burning.By making cooling-air be back to pressurized machine 100, the air exporting 104 places significantly reduces.Further, when the temperature of the necessary elevate air that effectively works in order to motor, cooling-air backflow can be limited by modulating valve 114A.

Sensor 153 can be pressure transducer, measures the air pressure formed in the intake manifold 121 of motor 120.The object of pressurized machine 100 is for motor 120 provides supercharging, thus allows motor 120 power stronger.Supercharging term pressure ratio provides, pressure ratio be pressurized machine before absolute air pressure be pressurized device 100 compress after the ratio of absolute air pressure.Therefore, it is very important that the air entering intake manifold 121 has suitable pressure.The intake manifold 121 that pressure transducer 153 can be positioned at motor 120 feeds back to controller 150 to provide.

The reading carrying out sensor 114,151,152 and 153 is transmitted to controller 150.Each reading received from sensor 114,151,152 and 153 and predetermined value can be made comparisons by controller 150.These predetermined values can be the optimum values calculated, and they are preserved in the controls, or these predetermined values can calculate in real time according to vehicle dynamic.

Such as, the reading carrying out sensor 151 can equal predetermined value.The present air amount that this means to enter motor and the air entering pressurized machine are best.Therefore, if controller 150 judges that the reading carrying out sensor 151 equals predetermined value, so just can not take measures.On the other hand, the reading carrying out sensor 151 may be not equal to predetermined value.The present flow rate or the temperature that this means the air entering motor or leave pressurized machine are not best.In this case, controller 150 can also send the signal utilizing actuator 114 to open or close valve 114A except other regulated signal.By opening or closing valve 114A, the temperature of pressurized machine can be regulated.By controlling backflow action, outlet pressure pulsation can be affected according to expected result.Except other working state, other control mechanism can also be implemented to regulate the rotating speed of pressurized machine 100.Similar judgement and adjustment can be made to remaining sensor.

Controller 150 regulates the air quantity in conduit 112 by the aperture of control valve 114A.Similarly, controller 150 can adjust other working state, the aperture of such as closure.By make backflow or the air that enters pressurized machine 100 there is suitable amount, the efficiency of supercharger systems 10 can be guaranteed.

Fig. 2 B and 2C illustrates alternative control mechanism 21 and 22.Control mechanism 21 corresponds to the system 11 of Figure 1B.Be similar to the description to Fig. 2 A, the controller 150 of Fig. 2 B can adjust backflow action.System 11 also can send a signal to bypass actuator 115 to control to walk around the air quantity of motor 120.It is more multi-control that this can realize the air quantity entering pressurized machine 100.

The multichannel actuator 116 that Fig. 2 C similarly controls multi-way valve 116A with custom tailored around to entrance 101 or the cooling air volume being supplied to runoff return port 122.

Engine air capacity demand can based on other vehicle operating status various, therefore, except with except the comparing of predetermined value, or substitutes it, can also calculate in real time.Therefore, the simplification control mechanism of Fig. 2 A, 2B and 2C can be strengthened be comprise additional sensor and feedback and can be bundled in other wagon control, such as, accelerate, go off course, tumble, slide, brake etc.Therefore, along with engine air capacity demand changes due to these other factorses, cooling-air backflow and bypass action can be regulated to export the air temperature at 104 places with custom tailored.

The impact testing to test cooling-air backflow is carried out under 14,000RPM.To utilize Fig. 3 that the result obtained in these experiments is described now.Plotted curve in Fig. 3 illustrates the relation between the temperature at supercharger outlet 103 place and obtainable pressure ratio.Fig. 3 draws out the curve of the laboratory data obtained under the rotating speed of 14,000RPM.The longitudinal axis represents the temperature of supercharger outlet 103, and transverse axis represents pressure ratio.When doing this experiment, thermoae limit is set to 150 degrees Celsius.Thermoae limit or Maximum operating temperature are one of parameters of pressure ratio for determining Roots type super charger.If the pressure increase making pressurized machine provide and do not raise air fed temperature, so much higher pressure ratio can be obtained.Inlet temperature is constant is 27 degrees Celsius.Pressurized machine used in experiment be Eaton company manufacture M45 Roots type super charger, with the example class shown in Fig. 5 seemingly.

Data shown in plotted curve be without the M45 pressurized machine of cool air reflux pressure ratio and have the pressure ratio of M45 pressurized machine of cool air reflux.The curve of the M45 pressurized machine without cool air reflux obtained tilts about 45 degree, than having the situation of cool air reflux more sharply.

These results show, for the thermoae limit of appointment, higher-pressure ratio appears in the M45 pressurized machine of cool air reflux.Fig. 3 illustrates, at 150 degrees Celsius, the pressure ratio without the M45 of cool air reflux is 2.2.In order to obtain the pressure ratio higher than 2.2, pressurized machine must be over its thermoae limit and runs, and this is unpractiaca due to the thermal expansion of parts and the interference of tolerance.But by having cool air reflux in M45 pressurized machine, pressure ratio is increased to about 4.5, but not super overheating limit.

Except test cooling for reflux air is on except the experiment of the impact of pressure ratio, the also impact of simulation backflow on temperature.The comparison of Fig. 4 A and 4B illustrates the impact of cooling-air on the air temperature at supercharger outlet place.This simulation carries out under the supercharger speed of 6000RPM.Fig. 4 A illustrates the analog result without the temperature distribution in the supercharger systems of cool air reflux.Air enters pressurized machine 100X and to be heated and discharged to intercooler 110X.Return-flow catheter 122Y allows the air inlet port 122X discharged.Air is heated by the pump action of pressurized machine 100X, and the air of therefore discharging is warmmer compared to inlet temperature.Given comprise pressure ratio be 2 and inlet temperature be the constant of 300K, simulation supercharger systems in temperature distribution (K).When measuring, outlet temperature, close to 435K, causes the temperature of 135K from the inlet to the outlet to raise.

On the other hand, the supercharger systems having cooling-air to reflux in Fig. 4 B presents less temperature and raises.Air enters pressurized machine 100 and is discharged to intercooler 110.After leaving intercooler, cooling-air is advanced through conduit 112 and is back to pressurized machine 100.Outlet temperature is 388K, and clean temperature rise is from the inlet to the outlet only 88K thus.Therefore, the cool air reflux in supercharger systems reduces the air temperature at supercharger outlet place.

Fig. 5 illustrates the model of the pressurized machine 100 that can be used in supercharger systems 10,11 and 12.Pressurized machine 100 is axial entrance, radial export-oriented.Inlet air flow path arrow illustrates, therefore, the air entering air inlet on the right side of the page is discharged at the triangular-shaped outlet 104 of page central authorities.Remove a part for shell to illustrate the inside of main casing 106.Pressurized machine 100 can be other Roots type super charger that such as M45 or Eaton company manufactures, and comprises two eddy current (TVS) type.Fig. 5 illustrates the cross section of pressurized machine 100, has the multiple runoff return port 122 communicated with each rotor.Pressurized machine 100 has two rotors 102,103, and rotor all has three blades.Two rotors 102,103 are placed in housing cavity 105.Runoff return port 122 can be placed in outlet every side and close to each rotor 102,103.By settling runoff return port 122 with between adjacent blades air being directed to each rotor, cooling-air can mix the temperature to reduce the air being just sent pressurized machine 100 effectively with air inlet.

Runoff return port 122 can be placed in main casing 106 to connect with recycling pipe 112.The foundry goods that main casing 106 can be formed as limiting entrance 101, export 104 and runoff and/or axial flow return port 122.Main casing 106 can comprise multiple the sections integrated, and main casing 106 can be combined with other shell part and form the air capsule of other work structuring around rotor, rotor pedestal, gear-box and pressurized machine 100.

In specification above, describe each preferred embodiment with reference to the accompanying drawings.But, it is evident that, can other remodeling various be made to them and change, and other embodiment can be implemented and do not depart from the relative broad range of claims.Therefore, this specification and accompanying drawing should be considered to be descriptive and nonrestrictive.

By considering this specification and practice of the present utility model, other embodiment will be apparent for a person skilled in the art.Such as, master motor intercooler may be had, as intercooler 110, and be exclusively used in other intercooler of each return-flow catheter 112 or return port 122.It is only exemplary that this specification and example should be seen as, and true scope of the present utility model and spirit are shown by claims.

Claims (39)

1. axial entrance, a radial exit type pressurized machine, is characterized in that comprising:
Tubular shell, described tubular shell comprises plane of inlet (IP) and pelvic outlet plane (OP), and wherein said plane of inlet is perpendicular to described pelvic outlet plane;
Rotor mounting recess (1030,1020), described rotor mounting recess is arranged in the internal surface of the entry wall (1063) being parallel to described plane of inlet;
Triangular-shaped outlet (104) in described pelvic outlet plane;
Entrance (101) in described plane of inlet; With
At least two axial flow return port (1222) in described plane of inlet (IP).
2. pressurized machine as claimed in claim 1, it is characterized in that, each in described at least two axial flow return port is notch, and this notch has the profile matched with the sections on involute.
3. pressurized machine as claimed in claim 1, it is characterized in that, described pelvic outlet plane (OP) also comprises at least two runoff return port (122).
4. the pressurized machine as described in claim 1 or 3, it is characterized in that, each in each and described at least two runoff return port in described at least two axial flow return port has four sides and these four sides are the one in the notch of circular arc, rectangular notch, oval pore or circular port.
5. the pressurized machine according to any one of claim 1-3, is characterized in that, also comprises header board (1060), and this header board is separated with described entry wall (1063) by adjustment distance (TD).
6. pressurized machine as claimed in claim 5, is characterized in that, also comprise the passage (1061) in described header board (1060), and described passage aligns with each in described at least two axial flow return port (1222).
7. pressurized machine as claimed in claim 5, it is characterized in that, also comprise the base plate (1071) between described entry wall (1063) and described header board (1060), described base plate makes described entrance (101) fluidly separate with described at least two axial flow return port (1222).
8. pressurized machine as claimed in claim 7, it is characterized in that, be also included in the supporting portion (1010) in described entrance (101), described base plate (1071) is abutted against in described supporting portion.
9. pressurized machine as claimed in claim 1 or 2, is characterized in that, the return port area A that described axial flow return port occupies in described tubular shell portdetermined by following formula:
Wherein, P 1inlet pressure, P 2the pressure maximum ratio of described outlet, T 1inlet temperature, T 2be outlet temperature, R is gas constant, N rPMbe the maximum (top) speed of the rotor in pressurized machine, unit is rev/min, V transferVolumebe transmitted volume of air, α refers to and determines inlet temperature T 1under the velocity of sound, γ be wait hold wait pressure ratio of specific heat.
10. pressurized machine as claimed in claim 9, is characterized in that, the desirable port area A that described axial flow return port occupies iPortat A portthe scope of to 4/4th times in.
11. pressurized machines as claimed in claim 10, is characterized in that, described desirable port area A iPorta porthalf to 2 times.
12. pressurized machines as claimed in claim 11, is characterized in that, described desirable port area A iPorta port2/3rds.
13. pressurized machines as claimed in claim 9, is characterized in that, are also included at least two runoff return port (122) in described pelvic outlet plane (OP), described return port area A portthe area that described in also comprising, at least two runoff return port occupy.
14. pressurized machines according to any one of claim 10-12, is characterized in that, be also included at least two runoff return port (122) in described pelvic outlet plane (OP), wherein said desirable port area A iPortalso occupied by described runoff return port (122).
15. 1 kinds of axial entrances, radial exit type pressurized machines, is characterized in that comprising:
Tubular shell, described tubular shell comprises plane of inlet (IP) and pelvic outlet plane (OP), and wherein said plane of inlet is perpendicular to described pelvic outlet plane;
Rotor mounting recess (1030,1020), described rotor mounting recess is arranged in the internal surface of the entry wall (1063) being parallel to described plane of inlet;
Inlet axis (IA), it is placed in the middle between described rotor mounting recess;
Triangular-shaped outlet (104) in described pelvic outlet plane;
Entrance (101) in described plane of inlet;
Rotor (102 with blade, 103), the rotor of each band blade comprises the spin axis parallel with described inlet axis (IA), wherein when described rotor rotates, described blade sequentially engages along described inlet axis (IA), wherein each blade reverses along the length of their respective rotors, and wherein these blades are set the time and seal relative to described outlet fluid for making described entrance; With
At least two return port (122,1222) in described tubular shell.
16. pressurized machines as claimed in claim 15, is characterized in that, described at least two return port are the axial flow return port (1222) in described plane of inlet (IP).
17. pressurized machines as claimed in claim 15, is characterized in that, described at least two return port are the runoff return port (122) in described pelvic outlet plane (OP).
18. pressurized machines as claimed in claim 15, it is characterized in that, described at least two return port are the axial flow return port (1222) in described plane of inlet (IP), and described pressurized machine also comprises at least two runoff return port (122) in described pelvic outlet plane (OP).
19. pressurized machines according to any one of claim 16-18, is characterized in that, the return port area A that described at least two return port occupy in described tubular shell portdetermined by following formula:
Wherein, P 1inlet pressure, P 2the pressure maximum ratio of described outlet, T 1inlet temperature, T 2be outlet temperature, R is gas constant, N rPMbe the maximum (top) speed of the rotor in pressurized machine, unit is rev/min, V transferVolumebe transmitted volume of air, α refers to and determines inlet temperature T 1under the velocity of sound, γ be wait hold wait pressure ratio of specific heat.
20. pressurized machines as claimed in claim 19, is characterized in that, the desirable port area A that described at least two return port occupy iPortat A portthe scope of to 4/4th times in.
21. pressurized machines as claimed in claim 20, is characterized in that, described desirable port area A iPorta porthalf to 2 times.
22. pressurized machines as claimed in claim 21, is characterized in that, described desirable port area A iPorta port2/3rds.
23. pressurized machines as claimed in claim 16, is characterized in that, each in described at least two axial flow return port is notch, and this notch has the profile matched with the sections on involute.
24. pressurized machines as described in claim 16 or 17, it is characterized in that, each in each and described at least two runoff return port in described at least two axial flow return port has four sides and these four sides are the one in the notch of circular arc, rectangular notch, oval pore or circular port.
25. pressurized machines as claimed in claim 15, it is characterized in that, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree completes air inlet phase, blade rotary 20-50 degree is to complete stop phase place, blade rotary 20-40 degree completes sealing phase place, and blade rotary 25-50 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.
26. pressurized machines as claimed in claim 15, it is characterized in that, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree is to complete air inlet phase, blade rotary 0-50 degree is to complete stop phase place, blade rotary 15-70 degree is to complete sealing phase place, and blade rotary 20-70 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.
27. pressurized machines as claimed in claim 15, it is characterized in that, the rotor of each band blade rotates with the blade on movable rotor, and blade rotary 210-280 degree is to complete air inlet phase, blade rotary 20-50 degree is to complete stop phase place, blade rotary 10-50 degree is to complete sealing phase place, and blade rotary 20-80 degree is to complete backflow phase place, and blade rotary 200-220 degree is to complete discharge phase place.
28. pressurized machines according to any one of claim 15,16,17,23 or 25-27, is characterized in that, each in described at least two return port is configured as to be opened at 10 to 15 degree of blade rotary.
29. pressurized machines according to any one of claim 15,16,17,23 or 25-27, is characterized in that, each in described at least two return port is configured as to be opened at 30 to 40 degree of blade rotary.
30. pressurized machines as claimed in claim 15, is characterized in that, are stopped by respective vanes completely when described at least two return port are sized to before blade rotary to the corresponding port in described at least two return port.
31. pressurized machines as claimed in claim 15, it is characterized in that, each blade has profile, and each in described at least two return port is configured as the sections of described blade profile.
32. pressurized machines as claimed in claim 15, is characterized in that, also comprise header board (1060), and this header board is separated with described entry wall (1063) by adjustment distance (TD).
33. pressurized machines as claimed in claim 32, it is characterized in that, also comprise the base plate (1071) between described entry wall (1063) and described header board (1060), described base plate makes described entrance (101) fluidly separate with described at least two return port (1222).
34. pressurized machines as claimed in claim 32, is characterized in that, also comprise the passage (1061) in described header board (1060), and described passage aligns with each in described at least two return port (1222).
35. pressurized machines as claimed in claim 34, is characterized in that, also comprise the recycling pipe (112) being connected to described passage (1061).
36. pressurized machines as claimed in claim 15, characterized by further comprising:
Intercooler, it includes an inlet and an outlet, described intercooler connect into from the outlet of described pressurized machine receive by the air that blows and connect into cooling and discharge the air that receives as return air; With
Conduit, the return port of pressurized machine described in described tubes connection and the outlet of described intercooler to receive described return air,
Wherein, the rotor of described band blade comprises rotatable the first rotor and rotatable second rotor,
Wherein, each in described the first rotor and the second rotor comprises at least three blades,
Wherein, between each adjacent blades, be formed with corresponding space,
Wherein, when space is aligned, described return port is orientated the cooling-air provided to adjacent space from described intercooler,
Wherein, when providing cooling-air to described adjacent space, described adjacent space is sealed relative to described entrance and described outlet.
37. pressurized machines as claimed in claim 36, is characterized in that,
Described the first rotor at least comprises the first blade and the second blade,
Described second rotor at least comprises Three-blade and quaterfoil,
Described at least two return port comprise the first return port and the second return port,
When return air is exposed to described second return port and the space between described Three-blade and described quaterfoil, described first return port by described first runner sealing, and
When described return air is exposed to described first return port and the Second gap between described first blade and described second blade, described second return port is sealed by described quaterfoil.
38. pressurized machines as claimed in claim 15, is characterized in that, described pressurized machine has the thermoae limit of 150 degrees Celsius and the outlet pressure of 4.4:1 and the pressure ratio of inlet pressure.
39. pressurized machines as claimed in claim 15, is characterized in that, each blade reverses 60-130 degree along the length of their respective rotors.
CN201420825880.1U 2013-10-31 2014-10-31 Axial entrance, radial exit type pressurized machine CN204646407U (en)

Priority Applications (8)

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US201361897928P true 2013-10-31 2013-10-31
US61/897928 2013-10-31
US201461991166P true 2014-05-09 2014-05-09
US61/991166 2014-05-09
US29/499,660 USD816717S1 (en) 2014-08-18 2014-08-18 Supercharger housing
IN2337/DEL/2014 2014-08-18
US29/499660 2014-08-18
IN2337DE2014 2014-08-18

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