CN102822471A

CN102822471A - Super-turbocharger having a high speed traction drive and a continuously variable transmission

Info

Publication number: CN102822471A
Application number: CN2010800658285A
Authority: CN
Inventors: E·万迪尼; B·T·布林克斯; M·B·莱利; J·W·布朗
Original assignee: VanDyne SuperTurbo Inc
Current assignee: VanDyne SuperTurbo Inc
Priority date: 2010-02-05
Filing date: 2010-02-05
Publication date: 2012-12-12
Anticipated expiration: 2030-02-05
Also published as: GB2489647A; DE112010005233T5; ES2453204B1; ES2453204A2; MX2012009009A; WO2011096936A1; ES2453204R1; CA2786580A1; AU2010345054B2; SE1250994A1; GB2489647B; GB201214265D0; CN102822471B; DE112010005233B4; JP5688417B2; JP2013519034A; AU2010345054A1; MX356972B

Abstract

A super-turbo charger utilizing a high speed, fixed ratio traction drive that is coupled to a continuously variable transmission to allow for high speed operation is provided. A high speed traction drive is utilized to provide speed reduction from the high speed turbine shaft. A second traction drive provides infinitely variable speed ratios through a continuously variable transmission. Gas recirculation in a super-turbocharger is also disclosed.

Description

Super turbosupercharger with high speed traction drive and continuous variable gearbox

The cross reference of related application

Present patent application is the U. S. application No.12/536 of application on August 5th, 2009; 421 partial continuous case; Said application requires the U.S. Provisional Patent Application No.61/086 of application on August 5th, 2008; 401 right, the whole teachings and the disclosure of said application are incorporated herein by reference.

Background of invention

Traditional turbosupercharger is by used heat and exhaust gas driven, and it is compelled to pass the exhaust driven gas turbine shell to turbine.Turbine is connected to compressor wheel through common turbine shaft.When turbine was run in exhaust, two wheels rotated simultaneously.The rotating tee overcompression device shell of compressor wheel sucks air, and it forces pressurized air to get into engine cylinder and realizes improved engine performance and fuel efficiency.The size that is used for the turbosupercharger of speed change/variable load application is fit to the maximal efficiency under the torque peak speed usually and reaches Peak torque so that produce enough to boost.Yet than under the low speed, turbosupercharger produces inadequate boosting and is used for the proper engine transient response.

In order to overcome these problems and the system that increases efficient to be provided, can use super turbosupercharger, the characteristic of said super turbosupercharger combining super pressurized machine and turbosupercharger.Super turbosupercharger is incorporated into and is mainly contained the super pressurized machine that benefits low speed and large torque and the benefit that only is of value to the turbosupercharger of high speed high pass filter usually.Super turbosupercharger combines turbosupercharger and can Engine torque be positioned over the gearbox that is used for super supercharging and elimination turbo on the turbine shaft.In case exhaust energy begins to provide than drive compression device more work, so super turbosupercharger regains excessive power through applying excess power to piston engine (passing through arbor usually).Therefore, super turbosupercharger provides value-added two benefits of low speed and large torque and high speed high pass filter fully from a system.

Brief summary of the invention

Therefore, embodiment of the present invention can comprise the super turbosupercharger that is coupled to motor, and it comprises: turbine, and it produces the turbine rotating mechanical energy by the exhaust enthalpy through said engine producing; Compressor, its compression suck air and response is supplied to said motor by the said turbine rotating mechanical energy of said turbine generation and the engine revolution mechanical energy that transmits from said motor with pressurized air; Axle, it has the end that is connected to said turbine and said compressor, and the central part with traction surface; Traction drive; It is arranged in around the said central part of said axle; Said traction drive comprises: a plurality of planet rolling barrels; It has a plurality of planet rolling barrel traction surface, and said planet rolling barrel traction surface and said axle traction surface circle connect and make and have a plurality of first traction interface between said a plurality of planet rolling barrel traction surface and the said traction surface; The annular cylinder, it is rotated through a plurality of second traction interface by said a plurality of planet rolling barrels; The continuous variable gearbox; It mechanically is coupled to said traction drive and said motor, and it is sent to the turbine rotating mechanical energy said motor and under the service speed of said motor, engine revolution mechanical energy is sent to said super turbosupercharger.

Embodiment of the present invention can also comprise a kind of method that between super turbosupercharger and motor, transmits rotating mechanical energy, and it comprises: the exhaust enthalpy by through said engine producing produces the turbine rotating mechanical energy in turbine; Compression sucks air and responds the said turbine rotating mechanical energy that produced by said turbine and by the engine revolution mechanical energy of said engine producing pressurized air is supplied to said motor; Axle is provided, and it has the end that is connected to said turbine and said compressor, and the central part with traction surface; Traction drive mechanically is coupled to the said axle traction surface of said axle; A plurality of planet rolling barrel traction surface of placing a plurality of planet rolling barrels make the said axle of its contact traction surface and between said a plurality of planet rolling barrel traction surface and said axle traction surface, set up a plurality of first traction interface; Placing annular cylinder makes it contact said a plurality of planet rolling barrel to make and between said a plurality of planet rolling barrels and said annular cylinder, set up a plurality of second traction interface; The continuous variable gearbox mechanically is coupled to said traction drive and said motor and said turbine rotating mechanical energy is sent to said motor and under the service speed of said motor, engine revolution mechanical energy is sent to said super turbosupercharger.

Embodiment of the present invention can also comprise a kind of method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust that first preliminary dimension is provided in said internal-combustion engine; The low pressure exhaust mouth of second preliminary dimension is provided in said internal-combustion engine, and said second preliminary dimension is in fact greater than said first preliminary dimension; Use the driving high-voltage super turbosupercharger of first portion at least from the high pressure gas of said high-pressure exhaust; To the inlet manifold to said internal-combustion engine be provided from the second portion at least of the said high pressure gas of said high-pressure exhaust; Use low pressure exhaust to drive the super turbosupercharger of low pressure from said low pressure exhaust mouth; To the air input end to said high pressure compressor be provided from the pressurized air of the output terminal of said low pressure compressor; Under predetermined pressure, will the inlet manifold to said internal-combustion engine be provided from the pressurized air of the output terminal of said high pressure compressor; Opening said high-pressure exhaust when the pressure in the said high-pressure exhaust during greater than said predetermined pressure makes the said second portion of said high pressure gas connect said internal-combustion engine recirculation.

Embodiment of the present invention can also comprise a kind of method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust that first preliminary dimension is provided in said internal-combustion engine; The low pressure exhaust mouth of second preliminary dimension is provided in said internal-combustion engine, and said second preliminary dimension is in fact greater than said first preliminary dimension; Use high pressure gas to drive the high-voltage super turbosupercharger from said high-pressure exhaust; Use low pressure exhaust to drive the super turbosupercharger of low pressure from said low pressure exhaust mouth; To the air input end to said high pressure compressor be provided from the pressurized air of the output terminal of said low pressure compressor; Under predetermined pressure, will the inlet manifold to said internal-combustion engine be provided from the pressurized air of the output terminal of said high pressure compressor; To guide to the inlet manifold of said internal-combustion engine from the said high pressure gas of the output terminal of said high-voltage super turbosupercharger; Opening said high-pressure exhaust during greater than said predetermined pressure when the pressure in the said high-pressure exhaust makes the said high pressure gas from the said output terminal of said high-voltage super turbosupercharger connect said internal-combustion engine recirculation.

Embodiment of the present invention can also comprise a kind of method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust that first preliminary dimension is provided in said internal-combustion engine; The low pressure exhaust mouth of second preliminary dimension is provided in said internal-combustion engine, and said second preliminary dimension is in fact greater than said first preliminary dimension; To provide from the high pressure gas of said high-pressure exhaust to the inlet manifold of said internal-combustion engine; Use low pressure exhaust to drive the super turbosupercharger of low pressure from said low pressure exhaust mouth; Under predetermined pressure, will the inlet manifold to said internal-combustion engine be provided from the pressurized air of the output terminal of said high pressure compressor; Opening said high-pressure exhaust when the pressure in the said high-pressure exhaust during greater than said predetermined pressure makes the said second portion of said high pressure gas connect said internal-combustion engine recirculation.

The accompanying drawing summary

Fig. 1 is the side view of the embodiment of super turbosupercharger.

Fig. 2 is the big figure such as perspective of embodiment of the super turbosupercharger of Fig. 1.

Fig. 3 A is the side perspective of the embodiment of illustrated super turbosupercharger among Fig. 1 and Fig. 2.

Fig. 3 B is the side cutaway view of another embodiment of super turbosupercharger.

Fig. 3 C is the side perspective of the modification of the embodiment of illustrated super turbosupercharger among Fig. 1, Fig. 2 and Fig. 3 A.

Fig. 4 to Fig. 9 is to use the various figure of the super turbosupercharger of multipath planet rolling barrel traction-driven embodiment.

Figure 10 is the diagram of another embodiment of high speed traction-driven.

Figure 11 and Figure 12 are the diagrams of the embodiment of traction continuously variable gearbox.

Figure 13 is the side cutaway view of another embodiment.

Figure 14 A is the schematic representation of the embodiment of super turbo charged gas re-circulation device.

Figure 14 B is the schematic representation of another embodiment of super turbo charged gas re-circulation device.

Figure 14 C is the schematic representation of another embodiment of super turbo charged gas re-circulation device.

Figure 14 D is valve stroke, flow velocity and cylinder pressure and the plotted curve of piston position of the embodiment of Figure 14 A to Figure 14 C.

Figure 14 E is cylinder pressure and the PV plotted curve of cylinder volume of the embodiment of Figure 14 A to Figure 14 C.

Figure 15 is the diagram of simulation BSFC improvement project.

Embodiment

Fig. 1 is to use the schematic representation of embodiment of the super turbosupercharger 100 of high speed traction drive 114 and continuous variable gearbox 116.As shown in fig. 1, super turbosupercharger 100 is coupled to motor 101.Said super turbosupercharger comprises turbine 102, and said turbine 102 is coupled to motor 101 through exhaust manifolds 104.Turbine 102 produced rotating mechanical energy before exhaust manifolds 104 receive thermal exhaust and relief opening 112, discharge exhaust.Catalytic type diesel particulate filter (not shown) can be connected between exhaust manifolds 104 and the turbine 102.Perhaps, said catalytic type diesel particulate filter (not shown) can be connected to relief opening 112.The rotating mechanical energy that is produced by turbine 102 is transferred into compressor 106 through turbine/compressor axle (such as the axle 414 of Fig. 4); Rotate the compressor fan that is arranged in the compressor 106; Its compressed air inlet 110 and with compressed air delivery to conduit 108, conduit 108 is coupled to the inlet manifold (not shown) of motor 101.As disclosed in above application reference, be different from turbosupercharger, super turbosupercharger is coupled to and advances system to transmit its energy to said propelling system or transmit energy from said propelling system.As the alleged propelling of this paper system can comprise motor 101, be furnished with the vehicle of motor 101 speed changer, be furnished with driving system or other application of the rotating mechanical energy that produces by motor 101 of the vehicle of motor 101.In other words, rotating mechanical energy can be sent to motor through (such as the speed changer or the driving system of the vehicle) coupling of at least one intermediate mechanical device or from super turbosupercharger, and vice versa.In the embodiment of Fig. 1, the rotating mechanical energy of super turbosupercharger couples directly to the arbor 122 of motor 101 through axle 118, pulley 120 and line belt 124.As shown in fig. 1 equally, high speed traction drive 114 mechanically is coupled to continuous variable gearbox 116.

In operation, the high speed traction drive 114 of Fig. 1 is mechanically to be coupled to turbine/compressor axle fixed ratio, high speed traction drive, uses traction interface that rotating mechanical energy is sent to turbine/compressor axle or transmits rotating mechanical energy from turbine/compressor axle.High speed traction drive 114 has fixed ratio, and it can be according to motor 101 and difference.For mini engine, need the big fixed ratio of high speed traction drive 114.

For littler motor, the compressor of super turbosupercharger and turbine must keep the flow demand of mini engine size and coupling compressor and turbine forr a short time.For littler turbine and littler compressor are suitably played a role, it must be with higher rmp rotation.For example, littler motor possibly need compressor and turbine with 300, the 000rpm rotation.For minimum motor (such as half liter of motor), super turbosupercharger maybe be with 900, the 000rpm rotation.Littler motor need be to avoid surge with a reason of the compressor of higher rpm levels operation.In addition, in order to operate with effective and efficient manner, the head velocity of compressor must just in time not reach velocity of sound.Because said top is not as the length in the littler compressor, the top of littler compressor is moved soon not as the top of big compressor under identical rpm.When the size of compressor reduces, the required rotational speed exponential type of valid function rises.Because it is about 100 that gear is limited to, 000rpm is so the gear train of standard can't be used for reaching the power that consumes under the required fair speed of the super turbosupercharger of motor car engine.Therefore, various embodiments use high speed traction drive 114 to increase power and from the turbine shaft received power.

Therefore, be reduced to the rotational speed that can depend on turbine/compressor and the rpm level that changes from the rotating mechanical energy of high speed traction drive 114, but the rpm level in the operating range that is in continuous variable gearbox (CVT) 116.For example, high speed traction drive 114 can have in 0rpm and 7, the output that changes between the 000rpm, and can change to 300 from 0rpm from the input of turbine/compressor axle, and 000rpm, or bigger.Continuous variable gearbox 116 is applied to motor 101 with rpm horizontal adjustemt to the arbor 122 of high speed traction drive 114 and the rpm level of pulley 120 with rotating mechanical energy, or extracts rotating mechanical energy with suitable rpm level from motor 101.In other words, continuous variable gearbox 116 comprises the interface that is used between motor 101 and high speed traction drive 114, transmitting rotating mechanical energy, under the suitable rpm level according to engine rotary speed and turbine/compressor rotational speed change.Continuous variable gearbox 116 can comprise the continuous variable gearbox of any required kind, its can be required the rotational speed operation and the ratio of rotational speed that has coupling arbor 122 or directly or indirectly be coupled to other mechanism of motor 101.For example, except this paper disclosed embodiment, can use two cylinder CVT and traction ball to drive and promote steel band CVT.

The embodiment who is suitable for as the continuous variable gearbox of disclosed continuous variable gearbox 116 among Fig. 1 is a disclosed continuous variable gearbox among Figure 11 and Figure 12.The United States Patent(USP) No. 7,540,881 that can comprise the people such as Miller of issue on June 2nd, 2009 as other embodiment of the continuous variable gearbox of the continuous variable gearbox 116 of Fig. 1.The Miller patent is the embodiment with the traction drive of planet ball bearing, continuous variable gearbox.It is about 10 that the traction drive of Miller is limited to, and 000rpm makes Miller continuous variable gearbox can't be used as the high speed traction drive, such as high speed traction drive 114.Yet the Miller patent discloses a kind of embodiment who uses traction drive and be suitable for being used as the continuous variable gearbox that can be used as the continuous variable gearbox 116 shown in Fig. 1 to Fig. 3 really.The William R.Kelley of on June 6th, 2006 issue, Jr.'s and the patent No.7 with Borg Warner of assigning, another embodiment of the open continuous variable gearbox that is fit in 055,507.Another embodiment of open continuous variable gearbox in the United States Patent(USP) No. 5,033,269 of the Smith of issue on July 23rd, 1991.In addition, United States Patent(USP) No. 7,491,149 also disclose a kind of continuous variable gearbox that will be suitable for as continuous variable gearbox 116.The Greenwood that announced on February 17th, 2009 etc. be the people's and assign and openly can be used as the embodiment of the use traction-driven continuous variable gearbox of continuous variable gearbox 116 with the United States Patent(USP) No. 7,491,149 of Torotrak Co., Ltd.All these patents are disclosed to be incorporated into content teaching by reference especially.Also explain another continuous variable gearbox 3 of being suitable for as continuous variable traction drive 116 to announce the European application No.92830258.7 that No.0517675B1 announces August 9 nineteen ninety-five.

The high speed traction drive of various kinds can be used as high speed traction drive 114.For example, the high speed planetary drive of disclosed high speed planet traction drive 406 and Figure 10 can be used as high speed traction drive 114 among Fig. 4 to Fig. 9.

The embodiment of the high-speed driving of public use gear in the people's such as Hiereth of the United States Patent(USP) No. announcement on March 24th, 2,397,941 and 1998 of the Birgkigt that announce April 9 nineteen forty-six the United States Patent(USP) No. 5,729,978.These patents are disclosed to be incorporated herein with content teaching by reference especially.These references use master gear and do not use traction drive.Therefore, even use by high polish, specially designed gear train, it is about 100 that the gear in these systems is limited to, 000rpm or littler rotational speed.Announced on November 1st, 2005 Kolstrup's and the United States Patent(USP) No. 6,960,147 of assigning with Rulounds Roadtracks Rotrex A/S a kind of planetary pinion that can produce the gear ratio of 13:1 is disclosed.The planetary pinion of Kolstrup is the embodiment of high-speed driving of appropriate location that can be used for the high speed traction drive 114 of Fig. 1.United States Patent(USP) No. 6,960,147 disclosed and contents teaching also are incorporated herein by reference especially.

Fig. 2 is the schematic side elevational perspective view of super turbosupercharger 100.As shown in Figure 2, turbine 102 has the exhaust manifolds 104 that receive the exhaust that is applied to turbofan 130.Compressor 106 has the air-pressure duct 108 that pressurized air is supplied to inlet manifold.Compressor shell 128 envelopes are enclosed compressor fan 126 and are coupled to air-pressure duct 108.Disclosed like preceding text, high speed traction drive 114 is the fixed ratio traction drive that are coupled to continuous variable gearbox 116.Continuous variable gearbox 116 live axles 118 and pulley 120.

Fig. 3 A is the side perspective of the embodiment of illustrated super turbosupercharger 100 among Fig. 1 and Fig. 2.Moreover shown in Fig. 3 A, turbine 102 comprises turbofan 130, and compressor 106 comprises compressor fan 126.An axle (not shown) that connects turbofan 130 and compressor fan 126 is coupled to high speed traction drive 114.Rotating mechanical energy is sent to driving gear 132 from high speed traction drive 114, and driving gear 132 is sent to CVT gear 134 and continuous variable gearbox (CVT) 116 with rotating mechanical energy.Continuous variable gearbox 116 is coupled to axle 118 and pulley 120.

Fig. 3 B is another embodiment's the schematic cross sectional view that is coupled to the super turbosupercharger 300 of motor 304.Shown in Fig. 3 B, turbine 302 mechanically is coupled through axle 320 with compressor 306.High speed traction drive 308 is sent to rotating mechanical energy driving gear 322 or receives rotating mechanical energy from driving gear 322.The specific embodiments of diagram high speed traction drive 308 among Fig. 3 B.Driving gear 322 transmits rotating mechanical energy between traction drive 308 and continuous variable gearbox 110.Also illustrate the specific embodiments of continuous variable gearbox 310 among Fig. 3 B.Axle 312, pulley 314 and line belt 316 transmit rotating mechanical energy between arbor 318 and continuous variable gearbox 310.

Fig. 3 C is the side-looking schematic cross sectional view of the modification of the embodiment of illustrated super turbosupercharger 100 among Fig. 1, Fig. 2 and Fig. 3 A.Shown in Fig. 3 C, turbine 102 is coupled through the axle (not shown) with compressor 106.High speed traction drive 114 is coupled to said axle.Rotating mechanical energy is sent to driving gear 132 from high speed traction drive 114, and driving gear 132 is sent to gearbox gear 134 with rotating mechanical energy.High speed traction drive 114, driving gear 132 and gearbox gear 134 can all be contained in the same enclosure.Gearbox gear 134 is connected to gearbox 140, and gearbox 140 can comprise manual gear case, CVT, d-axis, automatic gear-box or hydraulic gearbox.Then, gearbox 140 is connected to axle 118, and axle 118 is connected to pulley 120.Pulley 120 is coupled to and advances system.In alternate embodiment, pulley 120 is coupled to electric motor/generator 142.

Fig. 4 is to use the perspective schematic view of another embodiment of the super turbosupercharger 400 of the high speed traction drive 416 that is coupled to continuous variable gearbox 408.As shown in Figure 4, turbine 404 usefulness compressor/turbine shafts 414 mechanically are coupled to compressor 402.Between compressor/turbine shaft 414 and multipath traction drive 416, transmit rotating mechanical energy with the more detailed disclosed mode of hereinafter.Driving gear 418 transmits rotating mechanical energy between the CVT gear 420 of multipath traction drive 416 and continuous variable gearbox 408.Axle 410 and pulley 412 are coupled to continuous variable gearbox 408 and between continuous variable gearbox 408 and propelling system, transmit power.

Fig. 5 is the side-looking generalized section that is coupled to the multipath traction drive 416 of driving gear 418, and driving gear 418 then is coupled to CVT gear 420.Open in more detail like hereinafter, compressor/turbine shaft 414 has polished, hardening surface on central part, and the fixed star that said surface is used as in the multipath traction drive 416 drives.

Fig. 6 is the exploded view 600 of the embodiment of illustrated super turbosupercharger 400 among Fig. 4.As shown in Figure 6, turbine shell 602 ccontaining turbofan 604.Hot side cover plate 606 is installed near turbofan 604 and the main shell supporting element 608.The exhaust at the hot side cover plate of lip ring 610 sealings 606 places.Annular roller bearings 612 is installed in the annular cylinder 614.Compressor/turbine shaft 414 extends through main shell supporting element 608.Hot side cover plate 606 is connected with turbofan 604.Planet carrier ball bearing 618 is installed on the planet carrier 620.Multipath annular cylinder 622 is connected to planet carrier 620 rotatably.Fuel supply line 624 is used for supplying draw fluid to traction surface.Planet carrier 626 is mounted to planet carrier 620 and uses planet carrier ball bearing 628.Then, retaining ring 630 is installed in planet carrier 626 outsides.Cage 632 is installed between retaining ring 630 and the cold side cover plate 636.Compressor fan 638 is coupled to compressor/turbine shaft 414.Compressor shell 640 envelopes are enclosed compressor fan 638.Main shell supporting element 608 also supports continuous variable gearbox and driving gear 418.Various bearings 646 are used for installing driving gear 418 and main shell supporting element 608.The continuous variable gearbox comprises CVT lid 642 and CVT bearing plate 644.CVT gear 420 usefulness bearings 650 are installed in main shell supporting element 608 inside.Relative with CVT bearing plate 644, CVT bearing plate 652 is installed on the opposite side of CVT gear 420.CVT covers the various piece of 654 cover cap CVT devices.Axle 410 is coupled to the continuous variable gearbox.Pulley 412 is installed on the axle 410 and between axle 410 and propelling system and transmits rotating mechanical energy.

Fig. 7 is the primary clustering that separates of multipath traction drive 416 and the perspective view of turbofan 604 and compressor fan 638.As shown in Figure 7, compressor/turbine shaft 414 is connected to turbofan 604 and compressor fan 638, and passes the center of multipath traction drive 416.Multipath traction drive 416 comprises multipath planet rolling barrel 664,666 (Fig. 9), 668.These multipath planet rolling barrels are coupled to planet carrier 626 (Fig. 9) rotatably.Ball 656,658,660,662 places the inclined surface that is used for the ball slope on the retaining ring 630.Open in more detail like hereinafter, annular cylinder 614 is driven by the internal diameter of multipath planet rolling barrel 664,666,668.

Fig. 8 is the side cutaway view of multipath traction drive 416.As shown in Figure 8, compressor/turbine shaft 414 is formed the traction surface that is used as sun roller 674 by sclerosis and polishing, and sun roller 674 has the traction interface 676 that connects with multipath planet rolling barrel 664 boundaries.Multipath planet rolling barrel 664 is along 672 rotations of multipath planet rolling barrel axle.Multipath planet rolling barrel 664 contacts retaining ring 630 at planet rolling barrel 664 with 690 places, interface of retaining ring 630.691 places contact annular cylinder 614 to multipath planet rolling barrel 664 at the interface, and different with interface 691, there is different radial distances at interface 691 apart from multipath planet rolling barrel axle 672.The ball slope 630 that Fig. 8 also illustrates planet carrier 626 and intersects with ball 656, and the ball slope 631 of intersecting with ball 660.Ball 656,658,660,662 is wedged between the ball slope (such as ball slope 630) on shell (not shown) and the retaining ring 664.When moment of torsion was applied to annular cylinder 614, this caused retaining ring 664 mobile slightly on the sense of rotation of annular cylinder 614.This causes ball each ball slope that moves up, and such as ball slope 630,631, this then causes retaining ring 630 to be pressed against multipath planet rolling barrel 664,666,668.Because planet rolling barrel 664 tilts with the interface 691 of retaining ring 630; And the interface of multipath planet rolling barrel 664 and annular cylinder 690 tilts; So produce inside power on the multipath planet rolling barrel 664, this increases the traction at traction interface 676 places between multipath planet rolling barrel 664 and the sun roller 674 in generation power on the traction interface 676.In addition, in the interface 691 places generation power of multipath planet rolling barrel 664 with annular cylinder 614, this increases the traction at 691 places, interface.Equally as shown in Figure 8, compressor fan 630 all is coupled to compressor/turbine shaft 414 with turbofan 604.Equally as shown in Figure 8, annular cylinder 614 is coupled to driving gear 418.

Fig. 9 is the side cutaway view of multipath traction drive 416.As shown in Figure 9, sun roller 674 is rotated in the clockwise direction, as passing through shown in the sense of rotation 686.Multipath planet rolling barrel 664,666,668 has the external diameter cylinder surface, such as the external diameter cylinder surface 688 of multipath planet rolling barrel 664.These external diameter cylinder surface contact sun roller 674, this causes multipath planet rolling barrel 664,666,668 to rotate in the counterclockwise direction, such as the sense of rotation 684 of multipath planet rolling barrel 666.Multipath planet rolling barrel 664,666,668 also has the internal diameter cylinder surface, such as the internal diameter cylinder surface 680 of multipath planet rolling barrel 664.The internal diameter cylinder surface of each multipath planet rolling barrel contacts the cylinder surface 687 of annular cylinder 614.Therefore, planet rolling barrel 664 is formed in the traction interface that transmits rotating mechanical energy when applying draw fluid with the interface 678 of the cylinder surface 687 of annular cylinder 614.Interface between each of multipath planet rolling barrel 664,666,668 and the sun roller 674 also is formed in the applying traction interface that transmits rotating mechanical energy afterwards of draw fluid.

Pointed like preceding text about Fig. 8 and Fig. 9, retaining ring 630 generation power, said force urges multipath planet rolling barrel 664,666,668 produces traction towards sun roller 674.Each of multipath planet rolling barrel 664,666,668 is attached to planet carrier 626 rotatably with planet rolling barrel axle (such as the multipath planet rolling barrel axle 672 of multipath planet rolling barrel 664).These volumes of traffic that have slightly make multipath planet rolling barrel 664,666,668 to move slightly and generation power between the external diameter cylinder surface (such as the external diameter cylinder surface 688 of multipath planet rolling barrel 664) of sun roller 674 and multipath planet rolling barrel 664,666,668.Multipath planet rolling barrel 664 is towards the traction at the interface that also increases multipath planet rolling barrel 664,666,668 and annular cylinder 614 of moving of sun roller 674, and this is because the interface (such as interface 678) of multipath planet rolling barrel 664,666,668 and annular cylinder 614 tilts.Multipath planet rolling barrel 664,666,668 causes planet carrier 626 to rotate in the clockwise direction with the contacting of cylinder surface 687 of annular cylinder 614, the sense of rotation 682 shown in Fig. 9.Therefore, annular cylinder 614 rotates (such as sense of rotation 687) in the counterclockwise direction and drives driving gear 418 in the clockwise direction.

Figure 10 is the schematic cross section of another embodiment of high speed traction drive 1000.As shown in Figure 10, axle 1002 (it is turbine and the axle of compressor that connects in the super turbosupercharger) can be used as the sun roller in the high speed traction drive 1000.Planet rolling barrel 1004 is at traction interface 1036 place's engagement shafts 1002.Planet rolling barrel 1004 uses bearing 1008,1010,1012,1014 on axle 1006, to rotate.Equally as shown in Figure 10, the outer surface of carrier 1018 is arranged and be connected to gear 1016.Carrier 1018 is coupled to the shell (not shown) through the bearing 1032,1034 of allowable carrier 1018 and gear 1016 rotations.Retaining ring 1020,1022 comprises ball slope 1028,1030 respectively.Ball slope 1028,1030 is similar to the ball slope 630 shown in Fig. 7 and Fig. 8.When gear 1016 moved, ball 1024,1026 moved in ball slope 1028,1030 respectively, and forces retaining ring 1020,1022 inwardly toward each other.When ball 1024,1026 forces fixed ramp 1020,1022 inwardly toward each other the time, generation power between the surface of the retaining ring 1020,1022 at traction surface 1038,1040 places and planet rolling barrel 1004.As shown in Figure 10, the power that is produced by retaining ring 1020,1022 also forces planet rolling barrel 1004 downward, therefore generation power between the axle 1002 at traction surface 1036 places and planet rolling barrel 1004.Therefore, realize bigger traction in traction surface 1036 with traction surface 1038,1040 places.Draw fluid is applied to these surfaces, because draw fluid is heated owing to produce friction at traction surface 1036,1038,1040 places, and the friction at viscosity and increase traction surface place so draw fluid becomes.

High speed traction drive 1000 shown in Figure 10 can be surpassing 100, the high speed rotating of 000rpm, and said speed can't reach through gear train.For example, high speed traction drive 1000 maybe be with greater than 300, the rotation of the speed of 000rpm.Yet high speed traction drive 1000 is limited to the gear ratio of about 10:1 because of the physical restriction of size.High speed traction drive 1000 can be used three planet rolling barrels, such as the planet rolling barrel 1006 around axle 1002 radial arrangement.As shown in Figure 9, the size of planet rolling barrel is with respect to sun roller and limited.If the diameter of the planet rolling barrel among Fig. 9 increases, planet rolling barrel will be adjacent to each other so.Therefore, as shown in Figure 10, only the gear ratio of about 10:1 can reach with the planet traction drive, and shown in Fig. 7 to Fig. 9, the multipath planetary drive that is connected to the planet carrier can have up to 47:1 or bigger ratio.Therefore, if must be with 300, the 000rpm effectively more puffer of rotation needs compressor, and as Fig. 7 to Fig. 9 shown in, the traction drive of 47:1 ratio can be with 300 so, and the maximum rotational delay of 000rpm is extremely about 6,400rpm.Then, the continuous variable gearbox of master gear or traction can be used between the propelling system of high speed traction drive and motor, transmitting rotating mechanical energy.

Disclosed like preceding text, the high speed traction drive 1000 shown in Figure 10 can have big ratio as the 10:1.Axle 1002 the rotational speed of supposing the super turbosupercharger of mini engine is 300,000rpm, and 300 of so said axle, the 000rpm rotational speed can be reduced to 30,000rpm at gear 1016 places.Can use the continuous variable gearbox 116 of each kind, it uses the operation of master gear technology up to 30,000rpm.Traction-driven continuous variable gearbox (the traction-driven continuous variable gearbox 116 shown in Figure 11 and Figure 12) also can be used as the continuous variable gearbox 116 shown in Fig. 1.In addition, can realize with the multipath traction drive 416 shown in Fig. 4 to Fig. 9 up to the ratio of 100:1.Therefore; Maybe be with 900; 5 liters mini engine of the compressor of 000rpm operation can be reduced to 9,000rpm, and this is easily to be used in the rotational speed that advances coupling rotating mechanical energy between system and the turbine/compressor axle by various continuous variable gearboxes 116.

Figure 11 and Figure 12 diagram can be used as the embodiment of traction drive gearbox of continuous variable of the continuous variable gearbox 116 of Fig. 1.Traction-driven continuous variable gearbox shown in Figure 11 and Figure 12 through on raceway surfaces in a lateral direction

translation seat ring

1116,1118 operate; Said raceway surfaces has the radius of curvature that the contact position that causes ball bearing moves, and said moving then causes ball to come to drive seat ring 1122 with friction speed with the rotation of different rotary angle.In other words, the contact position of each of the said bearing on the raceway surfaces is owing to the transverse translation of

seat ring

1116,1118 changes, and this has changed the rotational speed of said bearing at the contact position place, explains in more detail like hereinafter.

As shown in Figure 11, input shaft 1102 is coupled to driving gear 132 (Fig. 3 A).For example, tooth bar 1104 can be bonded to the CVT gear 134 shown in Fig. 3 A.Therefore, the tooth bar of input shaft 1102 input gear 1104 can be coupled to super turbosupercharger through high speed traction drive 114, shown in Fig. 3 A.In this way, the input torque that advances system is in order to drive the tooth bar input gear 1104 of input shaft 1102.Input torque on the tooth bar input gear 1104 makes input shaft 1102 structure related with it (comprising input seat ring 1114) rotation on sense of rotation 1112.Input seat ring 1116 also responds by tooth bar 1166 and authorizes to the moment of torsion of importing seat ring 1116 and around running shaft 1106 rotations from input shaft 1102.The rotation on a plurality of ball bearings 1132 is authorized in the rotation of input shaft 1102, input seat ring 1114 and input seat ring 1116, this be because permanent seat ring 1120 stop ball bearings with the rotation at the point of contact place of permanent seat ring 1120.Input seat ring 1114 rotates with same angular velocity with input seat ring 1116, and this is because they are coupled through tooth bar 1116.Input seat ring 1114 causes ball bearing 1132 on the orientation of approximate vertical, to rotate with input seat ring 1116, and this is because ball bearing 1132 contact permanent seat rings 1120.The contact that ball bearing 1132 is supporting permanent seat ring 1120 also causes the peripheral precession of ball bearing 1132 around

seat ring

1114,1116,1118,1120.In the embodiment depicted in fig. 11, can exist in nearly 20 the ball bearing 1132 that rotates on the surface of

seat ring

1114,1116,1118,1120.Ball bearing 1132 contacts owing to driven the tangent line of setting up ball bearing 1132 on the output seat ring 1118 that is rotated in that causes by input seat ring 1114 and input seat ring 1116.The contact position that depends on the ball bearing 1132 on the output seat ring 1118,

input seat ring

1114,1116 can change with respect to the ratio of the rotational speed of output seat ring 1118.Output seat ring 1118 is coupled to output gear 1122.Output gear 1122 engages output gear 1124, and output gear 1124 then is connected to output shaft 1126.

Traction-driven continuous variable gearbox 1100 shown in Figure 11 changes four

seat rings

1114,1116,1118 that the mode of the ratio between input shafts 1102 and the output shaft 126 contacts with ball bearing 1132 through change, the relative position of the point of contact between 1120 is realized.The mode that the contact surface of

seat ring

1114,1116,1118,1120 and ball bearing 1132 changes is through changing the position of translation folder 1152.As shown in Figure 11, translation folder 1152 responds electric actuators 1162 and moves horizontally.Electric actuator 1162 has the axle that engages telescopic speed changer 1158 and make telescopic speed changer 1158 rotations.Telescopic speed changer 1158 has different screw thread kinds on inside and outside.The difference of the pitch of different screw thread kinds cause translation folder 1152 response electric actuators 1162 axle rotation and move horizontally, this authorizes the rotation in the telescopic speed changer 1158.The transverse translation of the translation folder 1152 that contacts with bearing folder 1164 causes the transverse translation of input seat ring 1116 and output seat ring 1118.In the embodiment shown in Figure 11, input seat ring 1116 can change about 1/10th inches with the transverse translation of output seat ring 1118.The translation of input seat ring 1116 and output seat ring 1118 changes the contact angle between ball bearing 1132 and the output seat ring 1118, and this changes mobile ratio or the speed of ball bearing 1132 in said seat ring because of the change of the contact angle between permanent seat ring 1120 and input seat ring 1114 and the input seat ring 1116.The combination of the change of the angle between the said seat ring allows that ball bearing 1132 and output exposure rate or the point of contact between the seat ring 1118 changes, this cause input shaft 1102 rotational speed 0% to up to the rotational speed of input shaft 1102 30% between velocity variations.The velocity variations of 0% to 30% output seat ring 1118 that is the rotational speed of input shaft 1102 provide can reach at output shaft 1126 places can adjust rotational speed on a large scale.

In

seat ring

1114,1116,1118, suitable clamping between 1120, spring 1154,1156 is provided in order to ensure ball bearing 1132.Spring 1154 produces chucking power between input seat ring 1114 and permanent seat ring 1120.Spring 1156 produces chucking power between input seat ring 1116 and output seat ring 1118.These chucking powers of supporting ball bearing 1132 remain in the whole translation distance of translation folder 1152.Telescopic speed changer 1158 has the screw thread that is connected to retaining thread device 1160 on internal surface.Retaining thread device 1160 is fixed to shell 1172 and the fixed position with respect to shell 1172 is provided, and makes that translation folder 1152 can be because of the different screw threads translation in the horizontal direction on the both sides of telescopic speed changer 1158.

Equally as shown in Figure 11, the swivel assembly of traction-driven continuous variable gearbox 1100 is all gone up the rotation 1128 of rotation and output gear 1122 at equidirectional (being sense of rotation 1112).Clamping nut 1168 is retained on appropriate location and loading spring 1156 and between permanent seat ring 1120 and input seat ring 1114, produce suitable diagonal angle pressure in advance with spring 1156.As shown in Figure 11, when 1152 horizontal translations are pressed from both sides in translation, there is the translation slightly of input shaft 1102, according to the angle of the seat ring 1114 to 1120 of contact ball bearing 1132.Tooth bar input gear 1104 allows that the translation on direction 1108,1110 moves, according to the point of ball bearing 1132 contact seat rings 1114 to 1120 and the said seat ring specific contact angle with respect to ball bearing 1132.Shell 1170 is bolted to shell 1172 tightly and holds spring 1154, and this produces the chucking power of appropriate amount between input seat ring 1114 and permanent seat ring 1120.As shown in Figure 11, the rotation that has in four

seat rings

1114,1116,1118,1120 of ball bearing 1132 advances 1131.As shown in Figure 11, the sense of rotation 1112 of axle 1102 causes the rotation of gear 1122 on sense of rotation 1128.

Figure 12 is the close up view of seat ring 1114 to 1120 and ball 1132, the operation of its diagram traction-driven continuous variable gearbox 1100.As shown in Figure 12, seat ring 1114 contacts ball 1132 forcefully at contact position 1134 places.Seat ring 1116 contacts ball 1132 forcefully at contact position 1136 places.Seat ring 1118 contacts ball 1132 forcefully at contact position 1138 places.Seat ring 1120 contacts ball 1132 forcefully at contact position 1140 places.Each of

contact position

1134,1136,1138,1140 is positioned on the lip-deep common great circle of ball 1132.Said great circle is arranged in the plane of the axle 1106 of the center that holds ball 1132 and axle 1102.Ball 1132 is around 1142 rotations of the running shaft at the center of passing ball 1132 and split the said great circle of holding

contact position

1134,1136,1138,1140.The running shaft 1142 of ball 1132 tilts with vertical shaft 1144 angled 1146.Each the tilt angle 1146 that is arranged in ball in the seat ring of the circumference of traction drive 1100 is identical.Mathematical relationship is set up in tilt angle 1146 between distance rates and peripheral velocity ratio.Distance rates be first distance 1148 with second distance 1150 between ratio, first apart from 1148 being perpendicular distances of 1134 from running shaft 1142 to contact position, second distance 1150 is perpendicular distances of 1136 from running shaft 1142 to contact position.This distance rates equals said peripheral velocity ratio.Said peripheral velocity ratio is the ratio between first peripheral velocity and second peripheral velocity; Wherein said first peripheral velocity is peripheral velocity and the common track peripheral velocity of ball 1132 and the difference other ball in said seat ring between of ball 1132 at seat ring 1114 places; And said second peripheral velocity is the difference of ball 1132 between the common track peripheral velocity of peripheral velocity on the seat ring 1116 and ball 1132, and is arranged in other ball in the said seat ring.The radius of curvature of each of seat ring 1114 to 1120 is not necessarily constant radius of curvature, and can change.In addition, each radius of curvature of said four seat rings not necessarily equates.

When

seat ring

1116,1118 when horizontal direction (such as transverse translation direction 1108) is gone up translation simultaneously; The velocity rate of the rotation of axle 1102 and sense of rotation 1112 change with respect to the rotation and the sense of rotation 1128 of gear 1122, and the translation of

seat ring

1116,1118 on horizontal direction 1108 causes first distance 1148 to increase and second distance 1150 reduces.Therefore, distance rates and peripheral velocity ratio change, and this changes the rotational speed of gear 1122 with respect to axle 1102.

As noted above, the continuous variable gear box output end contacts with the traction drive reducing gear gear that is connected to the turbocompressor axle.As noted above, can use at least two or three different types of traction drive deceleration system.Typical kind is the disclosed planetary traction drive that is used for high deceleration among Fig. 6 to Fig. 9 and Figure 10.If need big speed difference between turbine shaft and the planet rolling barrel, the embodiment of Figure 10 can only be used two cylinders rather than three so, changes so that obtain required gear ratio.

Under the situation of three cylinders, there is the deceleration restriction of about 10:1, and possibly needs the gearbox of about 20:1 to obtain at a high speed 250,000rpm operates, and it is needed 25 to be lower than the gearbox of 10:1,000rpm.Therefore, in Figure 10, two cylinder planet traction drive can be used in the appropriate location in three planetary drive systems, so that realize the required deceleration of High Speed System of smallest.Two cylinders also provide less inertia, because each cylinder is thought that said system increases a certain amount of inertia.For minimum inertia, two cylinders should be enough.The width of haulage drum slightly is wider than three cylinder embodiments.

Supporting the multipath planet rolling barrel that axle rolls and processing by elastic material, for example spring steel or other materials, said material is allowed cylinder a little distortion in outer cylinder.The application of spring-loaded cylinder can provide the essential pressure on the axle but can axes not seek the ability of its desirable rotating center.

When turbosupercharger was operated with hypervelocity, it had the balance constraint that causes a rotating center that must find himself.Said balance will be compensated by moving of central shaft.This moves and can be compensated by spring-loaded cylinder.Said spring-loaded cylinder can also allow that not it is made for extremely light weight with the thin steel band that very little inertia is supporting the axle operation through being made for.Tape thickness must be enough thick and on traction surface, give enough pressure and provide traction required normal force.Cam follower can be arranged in the cylinder, and said cam follower will be located each cylinder and made said fixed-site in system.Cylinder must be operated between outer cylinder and turbine/compressor axle with very straight linear array, but the key that reduces inertia is in light weight.Can use one or two cam follower that steel band is retained on the appropriate location, suitable said steel band is arranged in a linear and rests in the said system.

Annular cylinder 614 is connected to gear on outer surface makes said annular cylinder can power transmission gone into or transferred out multipath traction drive 416.Annular cylinder 614 can many modes be processed.Annular cylinder 614 may simply be the solid members that steel maybe can be gone into torque transfer or transfer out other suitable materials of multipath traction drive 416.Annular cylinder 614 can be by allowing that annular cylinder 614 processes for many materials of lightweight, but annular cylinder 614 must be processed by the surperficial material of traction drive that can be used as on the cylinder surface 687.Suitable cylinder surface 687 allows that planet rolling barrel 664,666,668 is through the traction transfer of torque.

Turbine/compressor axle 414 also must keep being point-device linear array.Turbine/compressor axle 414 linear array is in the enclosure allowed between top and the compressor shell of blade of compressor and is maintained the gap.Tighter gap increases compressor efficiency.More accurate position reduces the touch opportunity between turbocompressor fan 638 and the compressor shell 640.Need a kind of control to guarantee to exist minimum clearance by the method for supporting the thrust load that the compressor wheel pressurized gas causes.This can use the thrust-bearing (not shown) of fuel feeding or the bearing of the thrust-bearing of ball bearing or roller bearings kind to accomplish.

In turbosupercharger, be the purpose of reliability, bearing normally all has the Casing bearing of oil-gap in inboard and the outside, so as to allow turbine shaft when its harmonious rotation with himself centering.The requirement of balance of the turbosupercharger of high volume manufacturing is through using the double gap bearing to reduce.Because need the more accurate linear array of the axle of tighter gap and turbosupercharger, so used these kinds of bearings.Ball bearing is used for fixing compressor and turbine and be used for keeping better aliging with shell from the lateral movement perspective view is being seen.This can be accomplished by one or two ball bearing.Linear array by the bearing in the perimeter of oil pressurization is allowed said bearing floating and is allowed that said bearing finds the center.This influences the gap between shell, turbine and the compressor outward edge really, but allows the thrust clearance that keeps little.The turbine shaft bearing provides the 3rd restriction point to keep the linear array of cylinder.Cam follower in the middle of said cylinder can make said cylinder keep 120 degree each other.Each cylinder can use two little cam followers to eliminate the backlash that when power changes direction, causes.

Also can use bigger turbine.The diameter of turbine wheel can be made for greater than normal dia.Even can make the turbine external diameter greater than compressor wheel, and can not reach the top near the critical velocity of velocity of sound part, this is because exhaust density is lower than intake air and therefore velocity of sound is higher.This allows that exhaust produces more moments of torsion and do not have higher back pressure on turbine/compressor axle.Having high torque causes said turbine to regain than to be compressed into the required energy more energy of mouthful air.This produces than the energy more energy that can regain and transfer to motor.The unwanted more multipotency measuring cup from the same row air-flow of compression institute is sent to arbor and the lower fuel consumption of generation.

The guide vane that in addition, can use the control exhaust to bang into the entering angle of turbine wheel improves turbine efficiency.This makes peak efficiencies higher, but has shortened the velocity range that implementation efficiency depended on.Narrow velocity range is unfavorable for conventional turbosupercharger, and for the super turbosupercharger that the manager can provide essential speed controlling, is not problem.

Compare with the pressure that strides across compressor, the higher back pressure that strides across turbine can also produce unbalanced super turbosupercharger.For conventional turbosupercharger, this pressure difference is opposite.Having higher back pressure causes said turbine to regain than to be compressed into the required energy more energy of mouthful air.This produces than the energy more energy that can regain and transfer to motor.The high pressure EGR loop of diesel engine needs higher back pressure.High back pressure needs valve or restriction usually, therefore high back pressure ordinary loss energy, and this is because conventional turbosupercharger can't be uneven and do not exceed the speed limit.Increase back pressure and be unfavorable for petrol engine and natural gas engine, this is that this makes motor more possibly have the blast problem because it increases the air displacement of catching in the cylinder.

According to another embodiment, second turbine wheel can be positioned at and increase energy that is regained by said turbine and the fuel efficiency of improving engine system on turbine/compressor axle.Equally, second compressor wheel can be positioned at the boost potential that increases super turbosupercharger on the same axis and allow the middle cooling between the level.Therefore this makes inlet temperature colder and be used for givenly boosting and reducing NOx.

In addition, can provide the turbine blade cooling to connect the fin top and reduce the temperature in the high temperature application.This can be accomplished by the outer peripheral hollow airfoil top of said turbine.This special tip designs has increased turbine efficiency and has been provided for the path that cooling air passes said blade.Turbine airfoil cooling can also provide by stride across the pressurized air that shell is supplied to the dorsal part of turbine wheel from compressor side.In addition, can use heat pipe to cool off said turbine wheel and blade.

In addition, can use the moment of torsion softening installation on the power path.Can be so that before getting into shell, remove from motor or advance the moment of torsion of system to promote and the mode of not losing said energy makes the arbor energy or comes the rotating mechanical energy of self-propelled system to pass curved axis or promote softening installation (spring-loaded or deflection).Through influencing gearbox, reduce the Peak torque demand without the torque peak on the traction drive.Through eliminating these torque peaks, traction drive is more reliable, and this is because traction requirements is subject to the Maximum Torque in the system.Through minimizing these torque peaks on the traction drive, can minimize said traction-driven size and surperficial area of contact.Minimum surperficial area of contact maximizes the efficient of said system, and still can realize transmitting the required moment of torsion of continuous power.

Perhaps and according to another embodiment, can use at axle, line belt or eaten the variable speed traction drive design that the appropriate location that drives has fixed displacement hydraulic pump.This makes said system be easier to encapsulation, and this is particularly useful for the very large motor with a plurality of turbosupercharger.

In illustrated another embodiment, the second super turbosupercharger uses a gearbox as the mode that obtains the elevated pressures ratio in Figure 13, and as the mode that obtains colder inlet temperature through use second interstage cooler.This maybe because of the fixed speed ratio between two super turbosupercharger.The first super turbosupercharger 1302 has air inlet duct 1308 and compresses the air that is supplied to motor from air-pressure duct 1310.Exhaust manifolds 1314 receive the turbine that moves the first super turbosupercharger 1302 from the exhaust of said motor.Exhaust outlet conduit 1312 is discharged in exhaust.The first super turbosupercharger 1302 usefulness driving gears 1306 are coupled to the second super turbosupercharger 1304.

Figure 14 A diagram is used the schematic representation of another embodiment that carries into execution a plan of two super turbosupercharger (such as super turbosupercharger 1402 of low pressure and high-voltage super turbosupercharger 1404).The super turbosupercharger of standard is bad at when outlet valve is opened for the first time, to regain the high-voltage pulse that is produced by cylinder.Shown in Figure 14 A, regain in order to improve this promotion pressure, the high pressure gas valve port 1406,1408 of the motor of four valves separates with low pressure exhaust valve port 1410,1412.High-pressure exhaust 1406,1408 is directed to high-pressure turbine 1434 through high pressure gas manifold 1430, and the low pressure exhaust mouth is directed to low-pressure turbine 1420 through low pressure exhaust manifold 1428.Through changing the valve sequential in the high-pressure exhaust 1406,1408, make valve on the high-pressure exhaust 1406,1408 at first open and opening towards high-pressure turbine 1434, regain pulse energy better.Valve quick closedown on the high-pressure exhaust 1406,1408, and the valve of following on the low pressure exhaust mouth 1410,1412 was opened in whole period of exhaust stroke.Valve opening on the low pressure exhaust mouth 1410,1412 is towards low-pressure turbine 1420.This process has reduced the required work of piston when making the cylinder exhaust.This process improvement standby fuel efficiency, or the supplementary loss when eliminating standby at least.The outlet of high-pressure turbine 1434 also is connected to low-pressure turbine 1420.Catalytic type diesel particulate filter (not shown) also can be arranged in than before the low-pressure turbine.

Same shown in Figure 14 A, EGR conduit 1438 is connected to high pressure gas manifold 1430.EGR conduit 1438 is allowed to be guided through cooler 1440 and EGR valve 1442 from the part of the exhaust of high pressure gas manifold 1430 and is back to inlet manifold 1444.The exhaust from high pressure gas manifold 1430 through 1438 guidings of EGR conduit is led to the purpose that inlet manifold 1444 is used for exhaust gas recirculatioon.The exhaust of flowing through exhaust gas recirculatioon conduit 1438 assists to reduce the FT in the combustion chamber, after especially in cooler 1440, cooling off.Said exhaust contains wetly and other liquid, and its temperature of assisting to reduce combustion chamber is come the NOx discharging of therefore minimizing from motor.The amount of EGR gas is by 1442 controls of EGR valve.EGR valve 1442 can (such as through using throttle valve) be fixed the NOx that the is monitored discharging that maybe can depend on motor and change.

Same shown in Figure 14 A, high-pressure air leaks to inlet manifold 1444 from high pressure compressor 1432 through high pressure compressor manifold 1446.Therefore, inlet manifold 1444 keeps by the indicated predetermined high-pressure level of the output terminal of high pressure compressor 1432.In order to make recycle gas flow through EGR conduit 1438, the pressure in the high-pressure manifold 1430 must be higher than the pressure in the inlet manifold 1444, as indicated by the delivery pressure of high pressure compressor 1432.So; Valve in the high-pressure exhaust 1406,1408 is enough opened during the downward stroke of piston early, and at this moment residual pressure still is present in the piston in high pressure gas manifold 1430, to produce enough pressure and drives the exhaust of passing EGR conduit 1438 from high pressure gas manifold 1430.Disclosed like hereinafter, the valve in the high-pressure exhaust 1406,1408 exists the point of less energy loss to open in the process of downward driven plunger.Opening a little of high pressure valve early than bottom dead center, but surpass the maximum torque point of arbor upper piston, this upper boom roughly is 90 °.This point occurs in about 100 °.The cosine of an angle value of torque capacity and bar is proportional, makes that piston is low more when high pressure valve is opened, and the energy that loses during driven plunger is just few more.Yet, the residual pressure of residual q.s in the cylinder chamber, this can be discharged from the cylinder chamber by high pressure valve before arriving bottom dead center, and it can make it get into high-pressure turbine 1434 in order to the exhaust that drives in the EGR conduit 1438.Through using the said cylinder of high pressure valve preexhaust of high-pressure exhaust 1406,1408, a large amount of residual pressures in the cylinder were discharged from before opening low pressure exhaust mouth 1410,1412.When opening, low pressure exhaust mouth 1410,1412 can be discharged most of pressure from cylinder.So, the residual pressure in the cylinder passes EGR conduit 1438 in order to the guiding exhaust to be reduced the NOx discharging and drives high-pressure turbine 1434, and this has increased extra power and efficient for motor.

Same as Figure 14 A shown in, from the exhaust of low pressure exhaust manifold low-pressure turbine 1420 in order to the super turbosupercharger 1402 of driving low pressure.Combine to drive low-pressure turbine 1420 by the exhaust of high-pressure turbine 1434 discharging with low pressure exhaust from low pressure exhaust mouth 1410,1412.Exhaust from low-pressure turbine 1420 is discharged by relief opening 1436.Low-pressure turbine 1420 is coupled to low pressure compressor 1418, the intake air 1422 of low pressure compressor 1418 compression prearranging quatitys.Conduit 1424 is directed to pressurized air the input end of high pressure compressor 1432 from low pressure compressor 1418; The forced air that high pressure compressor 1432 is used for further compressing in 1424 produces the more pressurized air of high pressure, and the pressurized air of said more high pressure is directed to inlet manifold 1444 by high pressure compressor manifold 1446.

The change scheme of the embodiment shown in Figure 14 B diagram 14A.Shown in Figure 14 B, high-pressure exhaust 1406,1408 is bonded in the high pressure gas manifold that is coupled to high-pressure turbine 1434.In other words, be applied to high-pressure turbine 1434 from whole high pressure gas of high pressure gas manifold 1430 and drive high-pressure turbine 1434, this then drives high pressure compressor 1432.The pressurized air of high pressure compressor 1432 from the low pressure compressor 1418 reception conduits 1424 of the compression intake air 1422 of the super turbosupercharger 1402 of low pressure.The output of high pressure compressor 1432 is supplied to input manifold 1444 through high pressure compressor manifold 1446.Low pressure compressor 1418 is driven by low-pressure turbine 1420, and low-pressure turbine 1420 is driven by the low pressure exhaust in the low pressure exhaust manifold 1428, and said low pressure exhaust is by 1410,1412 dischargings of low pressure exhaust mouth.Exhaust from low-pressure turbine 1420 is discharged through relief opening 1436.The pressurized gas from high pressure gas manifold 1430 that drive high-pressure turbine 1434 are coupled to exhaust gas recirculatioon (EGR) conduit 1426 and transmit and are back to inlet manifold 1444.The pressure from the pressurized gas of high pressure gas manifold 1430 that drives high-pressure turbine 1434 can not reduce and have sufficiently high pressure substantially the exhaust from EGR conduit 1426 is pressed in the inlet manifold 1444.Figure 14 B provides the maximum of NOx gas to reduce, and this is owing to the whole in essence exhausts from high pressure gas manifold 1430 all are recycled to inlet manifold 1444.

Same shown in Figure 14 B, can use waste gas valve 1448 with high pressure gas from high pressure gas manifold 1430 bypass to EGR conduit 1426.Sometimes high pressure gas maybe be too warm and/or the exhaust that is under the pressure that can excessively drive high-pressure turbine 1434 possibly is provided.In this case, the part that can open high pressure gas of waste gas valve 1448 directly is supplied to EGR conduit 1426 from high pressure gas manifold 1430.In addition, can increase EGR valve 1450, it is connected to low pressure exhaust manifold 1428 with EGR conduit 1426.If enough air displacemenies are supplied with through EGR conduit 1426, the part of those gases can be directed to low pressure exhaust manifold 1428 from EGR conduit 1426 through EGR valve 1450 so.Then, can be used for operating low-pressure turbine 1420 through increasing inlet mainfold presure 1444 and increasing extra power from the too much gas of EGR conduit 1426 to motor.The use of EGR valve 1450 provides and can regain the extra mode that recycle gas comes to increase the operating efficiency of extra power and raising motor to motor.

Another modification of the embodiment of Figure 14 C pictorial image 14A and Figure 14 B.Shown in Figure 14 C, intake air 1422 is by low pressure compressor 1418 compressions.Pressurized air from low pressure compressor 1418 is supplied with inlet manifold 1444 by conduit 1424.Same as Figure 14 C shown in, do not use second high-pressure turbine and whole recycle gas to be recycled to inlet manifold 1444 through EGR conduit 1426 from high-pressure exhaust 1406,1408.Be bonded to from the exhaust of low pressure exhaust mouth 1410,1412 and operate low-pressure turbine 1420 in the conduit 1428.Then, discharge said exhaust at relief opening 1436 places.Therefore, be supplied to from whole gases that blow downwards of high-pressure exhaust 1406,1408 and be back to the bigger minimizing that inlet manifold 1444 produces NOx gas.Perhaps, EGR valve 1450 can be used for the part of the exhaust in the EGR conduit 1426 is directed to low pressure exhaust manifold 1428, and this has increased other power and reduced the recirculating gas scale of construction in the EGR conduit 1426 for low-pressure turbine 1420.EGR valve 1450 can be adjusted the air displacement that is supplied to low pressure exhaust manifold 1428 from EGR conduit 1426.If enough air displacement recirculation in EGR conduit 1426 reduces the NOx output of motor, this process can be useful so.

Figure 14 D is valve stroke, cylinder pressure and flow velocity and the plotted curve of piston position after the top dead.Shown in Figure 14 D, in the whole stroke procedure of piston, cylinder pressure 1450 steady decrease after top dead.The lift of high pressure valve 1456 produces high-pressure spray 1452.About 100 ° of rotations take place and produce from the big surge downwards of the high-pressure spray 1452 of high-pressure exhaust 1406,1408 (Figure 14 A, Figure 14 B and Figure 14 C) discharge in the lift of high pressure valve 1456.The lift of curve 1454 diagram low pressure valves.The low pressure valve lift produces lowpressure stream 1458 in low pressure exhaust mouth 1410,1412.Therefore, the cylinder pressure in the cylinder 1450 further reduces.

Figure 14 E is that piston moves down in cylinder and the PV plotted curve of cylinder pressure and cylinder volume when then moving up.Nearly null representation top dead, and the bottom dead center of 1 expression cylinder rotation.Two curves shown in Figure 14 E.The cylinder pressure of bad sharp circuit motor and the curve of volume are not used in curve 1464 expressions.Curve 1462 is that diagram relies the cylinder pressure of sharp circulation means and the curve of cylinder volume, shown in Figure 14 A to Figure 14 C.Shown in Figure 14 A to Figure 14 C, at point 1466 places, high pressure valve is opened on bad sharp circulation means, and pressure reduces.Point 1466,1468 expressions of the zone between 1470 are through opening the energy that said high pressure valve loses.Yet,,, rely the pressure that is reduced under the pressure in the sharp circulation means in the Fei Laili circulation means and at the pressure that in the whole process of point 1474, keeps below said Fei Laili circulation means at point 1472 places as pointed among Figure 14 E.1472 and point 1474 between, have less pressure in the cylinder, this causes when the less back pressure of cylinder on putting 1472 cylinders when moving to a little 1474.Pass through under lower pressure the mobile energy of practicing thrift of piston in the cylinder by a large amount of zones indication between bad sharp cyclic curve 1462 and the ordinary curve 1464 of 1478 indications between the point 1472 and 1476.

In alternate embodiment, super turbosupercharger can be used as the extraction pump that is used for reprocessing, and is used for motor and eliminates the need of the separate pump only be used for combustion furnace.

In another embodiment, provide manager's (not shown) to prevent excessive acceleration, keep compressor to avoid the maximal efficiency of surge condition and control turbine and compressor.It is unique that super turbosupercharger is compared with conventional turbosupercharger, and this is because the peak value of the peak value of turbine efficiency and compressor efficiency can be under identical speed.Boost demand and control this peak efficiencies speed and can be molded and be programmed among the e-management person for given.Actuator can provide management, but the electric shift case does not need actuator.

In another embodiment, be used for the interior vacuum of fuel loading system pulling shell of super turbosupercharger, and therefore reduce the aerodynamic losses of high-speed assembly.

In another alternate embodiment, the super turbosupercharger of double clutch comprises the self-shifting manual transmission.This gearbox is speed change very reposefully, and this is because it all has clutch on two ends.Fig. 3 C diagram can have many different types of gearboxes.

In another embodiment, be used for gearbox and from the traction drive of the deceleration of turbine shaft.Use ball bearing, draw fluid is also as oiling agent.During super supercharging, system improve load receive, reduce soot emissions, provide the low side moment of torsion up to 30% increase and peak value power up to 10% increase.At the turbine Assemble Duration, it is improved up to 10% saving of fuel rate and control back pressure that system provides.For the motor downsizing, system provides more low side moments of torsion of 30% of allowing motor little 30% to 50%, have lower engine quality and 17% or more improved motor vehicle fuel saving rate.Figure 15 diagram is used for the simulation BSFC improvement project of natural gas engine.

Catalyzer, DPF or even combustion furnace add the higher temperature of temperature that turbine the place ahead that DPF also can be positioned at super turbosupercharger is heated to exhaust ratio engine.Higher temperature makes air expansion, even further makes the flow rate that strides across turbine higher.About 22% of this heat increase can change the mechanical work that strides across super turbosupercharger into, presents 80% turbine efficiency.The more a large amount of exhaust meeting that is supplied to turbine slow down the turbine response and even produce bigger turbo, but super turbosupercharger overcomes this problem with the traction drive 114 of driving pressure response with continuous variable gearbox 116.The similar techniques of public use catalyzing type purifier among the people's such as Van Dyne of application on July 24th, 2009 the international patent application No.PCT/US 2009/051742 that is entitled as " using super turbosupercharger to improve piston-engined fuel efficiency " (" Improving Fuel Efficiency for a Piston Engine Using a Super-Turbocharger "), said application is disclosed to be incorporated herein with content teaching by reference especially.

Figure 16 is the illustrated simplification single line drawing that forms an embodiment of high efficiency, super turbo charged engine system 1600.To understand from following description like those skilled in the art; This super turbo charged engine system 1600 is specially adapted to the petrol engine of more employed spark ignitions in DENG and passenger vehicle and the commercial car, and the exemplary embodiment of therefore this paper discussion uses this environment to help understanding of the present invention.Yet, should recognize that the embodiment of system 1600 is applicable to other operating environments, for example,, adopt these embodiments should be in order to explain rather than in order to limit such as continental rise generator and other continental rise motor.

As shown in Figure 16, super turbosupercharger 1604 comprises turbine 1606, compressor 1608 and gearbox 1610, and gearbox 1610 is coupled to the arbor 1612 of motor 1602 or advances other part of system.Though do not need in all embodiments, embodiment shown in Figure 16 comprises that also interstage cooler 1614 improves the next power that can get from motor 1602 that further improves of density that is supplied to the air of motor 1602 from compressor 108.

Super turbosupercharger has some advantage of turbosupercharger.Turbosupercharger is used the turbine by the exhaust gas drive of motor.This turbine is coupled to compressor, and said compressor compresses is supplied to the intake air in the cylinder of motor.Turbine in the turbosupercharger is by the exhaust gas drive from motor.So, when for the first time quickening until existing enough thermal exhausts to come rotary turbine to be that the compressor that mechanically is coupled to turbine is provided with power and produces when enough boosting, motor stands the sluggishness of boosting.In order to minimize sluggishness, use less and/or lighter turbosupercharger usually.The less inertia of the turbosupercharger of lightweight allows that it rotates very apace, thereby minimizes the sluggishness on the performance.

Unfortunately, the turbosupercharger of this less and/or lightweight possibly exceed the speed limit when producing a large amount of blast airs and temperature in high engine speeds operation period.In order to prevent this hypervelocity, typical turbosupercharger comprises the waste gas valve in the outlet pipe that is installed in the turbine upper reaches.Said waste gas valve is the pressure actuated valve that when the delivery pressure of compressor surpasses predetermined limit value, shifts turbine some exhausts on every side.This limiting value is set in the pressure that the said turbosupercharger of indication will exceed the speed limit.Unfortunately, this causes having wasted the part of the energy that can get from the exhaust of motor.

Should recognize that traditional turbosupercharger sacrifice low end performance is used for high-end power, has developed the device that is known as super turbosupercharger.The United States Patent(USP) No. 7 that is entitled as " super turbosupercharger " (" Super-Turbocharger ") of issue on February 17th, 2009; 490; Describe this super turbosupercharger in 594, this patent is disclosed to be incorporated herein with content teaching by reference especially.

In the application of quoting like preceding text discussion, in super turbosupercharger, low engine speed operation period when the engine exhaust of heat can't be used for driving turbine inadequately, compressor is driven through gearbox by the engine crankshaft that is coupled to motor.The mechanical energy that is supplied to said compressor by said motor reduces the turbo problem that the conventional turbine pressurized machine is suffered, and allows use more greatly or the more turbine and the compressor of efficient.

Super turbosupercharger 1604 operations shown in Figure 16 are not to suffer the turbo problem of conventional turbine pressurized machine low side and not to be wasted in the high-end energy that can get from the engine exhaust heat that is supplied to turbine 1606 from compressor 1608 supplied with compressed air to motors 1602.These advantages provide because of comprising super turbosupercharger gearbox 1610; During the various operator schemes of motor 1602, super turbosupercharger gearbox 1610 can extract power and supplying power to engine crankshaft 1612 come difference drive compression devices 1608 and loading turbine 1606 from engine crankshaft 1612.

Between the starting period; When the conventional turbine pressurized machine owing to lacking enough power from motor and drive turbine and suffer sluggishness; Super turbosupercharger 1604 provides super supercharging behavior, and gaining impetus drive compression device 1608 through super turbosupercharger gearbox 1610 from arbor 1612 thus is that motor 1602 provides enough boosting.When said motor reaches speed and when the amount of power that the engine exhaust heat can get is enough to drive turbine 1606, reduces from the amount of power that arbor 1612 obtains through gearbox 1610.After this, turbine 1606 continuation supplying power to compressors 1608 make its compression intake air and give 1602 uses of motor.

When engine speed increased, the amount of power that can get from the engine exhaust heat increased to the point that turbine 1606 the conventional turbine pressurized machine wherein can hypervelocity.Yet; Use super turbosupercharger 1604; Provided to the too much energy of turbine 1606 by the engine exhaust heat to be led to engine crankshaft 1612 through gearbox 1610, making compressor 1608 remain on that suitable speed comes simultaneously is desirable the boosting of motor 1602 supplies.The outputting power that can get from the exhaust gas heat of motor 1602 is big more, and the power that is produced by turbine 1606 that is led to arbor 1612 through gearbox 1610 is many more, keeps simultaneously boosting from the best that compressor 1608 can get.Turbine 1606 this loading through gearbox 1610 prevents the efficient of the power that turbine 1606 hypervelocities and maximization are extracted from engine exhaust.So, do not need traditional waste gas gate.

Though in the super turbo charged application of tradition, can be subject to the amount of power that can get in order to the amount of power strictness that drives turbine 1606 from engine exhaust; If but can use fully and/or can have additional supply of heat energy and the mass flow to turbine blade, turbine 1606 can produce obviously more power so.Yet turbine 1606 can't be operated on specified temp and not have damage, and mass flow is subject to the exhaust of coming out from motor 1602 traditionally.

Recognize this point, the embodiment of system 1600 is through protecting turbine 1606 to avoid the high temperature transition at turbine 1606 placed upstream catalytic type diesel particulate filters 1616.In one embodiment, the catalytic type diesel particulate filter is placed on the turbine upper reaches near gas exhaust manifold, and this realization causes the exothermic reaction of the increase of delivery temperature during the lasting high speed of motor or load operation.Use catalytic type numeral particulate filter, can regain energy from coal smoke, hydrocarbon and carbon monoxide and come to increase power for the super turbosupercharger that is positioned at catalytic type numeral particulate filter 1616 downstream in 1616 burnings of catalytic type diesel particulate filter.Can be from conventional diesel particulate filter or through using circulation catalytic type numeral particulate filter to regain energy with very limited circulation capacity of 100% coal smoke collection rate almost.Circulation catalytic type numeral particulate filter is a kind of diesel particulate filter of only collecting only about half of coal smoke and second half being passed.Two kinds of digital particulate filters all are that catalytic type is so that burning has effulent under the low temperature of appropriateness.The catalysis of numeral particulate filter is to realize through provide the platinum coating to guarantee that coal smoke, hydrocarbon and carbon monoxide burn at low temperatures for the particulate filter element.In addition, can use diesel particulate filter and burner that the coal smoke of the digital particulate filter at the super turbosupercharger upper reaches is burnouted.Petrol engine does not have enough coal smokes usually needs diesel particulate filter.Yet the direct injection engine of some gasoline produces enough coal smokes and other particle, therefore uses the particulate filter possibility useful, and can launch to use the catalytic type diesel particulate filter with mode disclosed herein.

For coolant exhaust before arriving turbine, a compressed-air actuated part that is produced by compressor directly is supplied in the exhaust at the turbine upper reaches through control valve 1618, and is added into the engine exhaust that leaves catalytic type diesel particulate filter 1616.As described in greater detail below, colder intake air expands and cools off said exhaust and be blast air increase additional mass, and this has increased extra power for turbine 1606.When colder air was provided to temperature that thermal exhaust makes the mix flow that arrives turbine 1606 and keeps being in optimum temperature, the energy and the mass flow that are delivered to said turbine blade also increased.This has significantly increased the power that is provided with driving engine crankshaft by said turbine.

In order not disturb the chemical reaction in the super turbosupercharger 1616, compressor feedback air is added into catalytic type diesel particulate filter 1616 downstream.In this embodiment, the temperature that engine exhaust passes catalytic type diesel particulate filter 1616 and said exhaust raises because of exothermic reaction.Then, said compressor feedback air is added and expands and makes the total mass flow that is supplied to said turbine increase.The compressed feedback air quantity that embodiment of the present invention control is provided with coolant exhaust and drives said turbine is guaranteed to be transported to said turbine than the combination of cold compression feedback air and engine exhaust with the optimum temperature that is used for turbine blade and operates.

Because the catalytic type diesel particulate filter 1616 shown in Figure 16 has recently from the big thermal mass of the exhaust of motor 1602, so originally catalytic type diesel particulate filter 1616 is operating as the thermal center air valve, it prevents that the high temperature thermal spike from arriving turbine 1606.Yet,, be higher than the delivery temperature that gets into catalytic type diesel particulate filter 1616 so leave the delivery temperature of catalytic type diesel particulate filter 1616 owing to be heat release in the reacting quintessence in the catalytic type diesel particulate filter 1616.As long as the delivery temperature that gets into turbine keeps below the maximum operating temp of turbine 1606, just do not have problems.

Yet,, can surpass the maximum operating temp of turbine 1606 from the discharge temperature of the transformation exhaust of catalytic type diesel particulate filter 1616 in the lasting high speed of motor 1602 and high capacity operation period.As indicated above, the delivery temperature of discharging catalytic type diesel particulate filter 1616 reduces because of a compressed-air actuated part of supplying from compressor 1608 through feedback valve 1618, and mixes with the exhaust of discharging catalytic type diesel particulate filter 1616.Significantly improved saving of fuel rate does not realize as freezing mixture through under this type situation, not using fuel, as in legacy system, doing.In addition, the operation of gearbox is controlled allows the compressor 1608 enough air supplies of supply and is that motor 1602 provides the best to boost and through feedback valve 1618 compressed feedback air to turbine 1606 is provided.Cause is led to arbor 1612 through the caused too much power that is produced by turbine 1606 of the mass flow of the compressed-air actuated increase of said turbine through gearbox 1610, still further improves fuel efficiency.

From the compressed-air actuated output temperature of compressor 1608 usually between about 200 ° of C to 300 ° of C.Conventional turbine can be come the gas extraction power from about 950 ° of C by optimum operation, but can higher and non-warping or possible breakdown.Because the materials limitations of turbine blade is issued to best power source at about 950 ° of C.Because material is limited to about 950 ° of C with delivery temperature, increase the performance that the mass flow that strides across turbine has improved said turbine so supply more air down in temperature extremes value (for example 950 ° of C).

Though help to reduce the delivery temperature of coming out at the compressed feedback air stream of 200 ° of C to 300 ° of C, should recognize when temperature and mass flow are in the thermoae limit value of turbine 1606 by maximization and can supply maximum power from turbine 1606 from catalytic type diesel particulate filter 1616.So, in one embodiment, the feedback air quantity is controlled to make the combination of exhaust and feedback air remain under the maximum allowable operating temperature (M.A.O.T.) of turbine or near said maximum allowable operating temperature (M.A.O.T.), therefore maximizes or significantly improve the amount of power that is delivered to turbine.Because it is that 1602 supply the bests are boosted and through feedback valve 1616 supplied with compressed devices feedback air that compressor 1608 does not need all these too much power usually; So said too much power can be transferred into the arbor 1612 of motor 1602 through gearbox 1610, therefore improve the total efficiency or the power of motor 1602.

As discussed above, in one embodiment, compressor feedback air uses catalytic type diesel particulate filter 1616 as the thermal buffer between motor 1602 and the turbine 1606 through the connection of feedback valve 1618.So, the air supply from said compressor is provided at the downstream of catalytic type diesel particulate filter 1616 so that do not interrupt the chemical reaction in the catalytic type diesel particulate filter 1616.Promptly; In the embodiment of using catalytic type diesel particulate filter 1616; Can cause too much oxygen to be provided to catalytic type diesel particulate filter 1616 at catalytic type diesel particulate filter 1616 supplied upstream compressors feedback air, prevent that thus catalytic type diesel particulate filter 1616 from producing the required chemical reaction of proper handling.

Reach the optimum efficiency of the power that produces by turbine 1606 when maximizing (in the material limits value at turbine self) owing to the temperature of feeding back the gaseous mixture of the exhaust on air and the turbine blade when compressor; So the compressor feedback limited amount of air through feedback valve 1618 gets into does not make it significantly be lower than this optimum temperature so that do not reduce temperature.Because catalytic type diesel particulate filter 1616 produces more heat energy through exothermic reaction and be increased to the temperature more than the maximum operating temp of turbine 1606 from the temperature of the transformation exhaust of catalytic type diesel particulate filter 1616; So can be through the more compressor feedbacks of feedback valve 1618 supplies air, said compressor feedback air increases mass flow and the energy that is supplied to turbine 1606.Because the amount of the heat energy that is produced by catalytic type diesel particulate filter 1616 reduces; So the amount by the compressor feedback air of feedback valve 1618 supply also can reduce; So that avoid supply than required more air, this causes the temperature of maintenance gaseous mixture under optimum operation condition.

In another embodiment, system uses feedback valve 1618 to be used for the anterior exhaust of turbine that is back under the low speed high capacity serviceability supplying with than cold compression device air, to avoid the surge of compressor.Because motor rotates with slow rpm and does not need too many intake air stream, thus when compressor pressure uprise but the mass flow of allowing in the motor when low, the surge of generation compressor.The compressor surge (aerodynamic force stall) that is caused by the low air flow that strides across compressor blade causes the efficient of compressor very rapidly to descend.In the situation of conventional turbosupercharger, enough surge meetings are stopped the rotation turbine.In the situation of super turbosupercharger, can use power from engine crankshaft to promote compressor and make its surge.Open feedback valve 1618 and allow that compressed-air actuated part feedback is around motor.This feedback flow makes compressor avoid surge and allows that higher boosting arrives motor 1602, allows that thus motor 1602 produces the ratio more power of issuable power under low engine speed usually.Pressurized air is injected the anterior exhaust of turbine preserve the total mass flow through compressor, therefore all flow to and reach turbine, this has minimized the super required power of high boost level that is pressurized to of motor.

In another embodiment, can comprise that extra cold start-up control valve 1620 is used for the operation during rich engine cold-start.During this engine cold-start, generally include too much unburned fuel from the exhaust of motor 1602.Because this rich mixture and non-stoichiometry are so catalytic type diesel particulate filter 1616 can not fully reduce the unburned hydrocarbons (UHC) in the exhaust.During this period, cold start-up control valve 1620 can be opened the input end that compressor feedback air to catalytic type diesel particulate filter 1616 is provided and supplies required extra oxygen and make rich mixture drop to the stoichiometry level.This allows that the weight of catalytic type diesel particulate filter 1616 alleviates and more effectively reduce the discharging between the cold start-up active stage quickly.If not having, motor standby, so conventional turbosupercharger do not boost to supply the feedback air.Yet the speed change ratio of gearbox 1610 can be given the enough speed of compressor by adjustment and produce air stream and cross the required pressure of valve 1620.So; The ratio that control signal 1624 can be used for adjusting gearbox 1610 makes during standby, especially during cold start-up, can made it flow through cold start-up valve 1620 and lights catalytic type diesel particulate filter 1616 with enough amount of oxygen for compressor 1608 provides enough rotational speeies to compress enough air by engine-driving axle 1612.

The demand of extra oxygen is limited usually in the cold start-up activity, and only continues 30 seconds to 40 seconds usually.Many vehicles generally include and separate extraction pump and at supply oxygen between the cold start-up active stage, compare with the required limited amount of time of this extraction pump operation, need great amount of cost and weight.Through replacing separating extraction pump, a large amount of cost savings, weight savings and complexity saving have been realized with simple cold start-up control valve 1620.Because super turbosupercharger 1604 can be through the speed of gearbox 1610 control compressors 1608, so cold start-up control valve 1620 can comprise simple close/open valve.Then, can be controlled at air supplied amount between the cold start-up active stage in the speed of control compressor 1608 under the operation of control signal 1624 through gearbox 1610.

If fuel is used as in the motor and/or is used for the freezing mixture of catalytic type diesel particulate filter 1616 and no matter to the negative effect of fuel efficiency, cold start-up control valve 1620 can also use in excessive temperature operation period so.In this case, cold start-up control valve 1620 can be supplied required extra oxygen and rich exhaust descended be back to the stoichiometry level and allow that catalytic type diesel particulate filter 1616 suitably reduces unburned hydrocarbons discharging in the exhaust.This provides big advantages for the environment on the previous system.

During cold start-up control valve 1620 in the embodiment of close/open valve, the air supply that cold start-up control valve 1620 changes supply can be modulated by system, so that make exhaust drop to the stoichiometry level therein.The variable-flow control valve of other kind also can be used for accomplishing identical function.

Figure 16 also discloses controller 1640.The operation of controller 1640 Control and Feedback valves 1618 and cold start-up valve 1620.Controller 1640 operations are to flow through the air quantity of feedback valve 1618 under the different situations of optimization.Describe like preceding text, the air quantity that flows through feedback valve 1618 is to obtain the needed minimum air flow amount of special required situation.Have the special state of two kinds of its middle controller 1640 operational feedback valves 1618, said situation is: 1) be similar to low rpm, the high capacity of motor for the surge limit of the compressor of the given demand of boosting; With 2) temperature of gaseous mixture is similar to the turbine 1606 that gets under the high rpm high load condition.

As shown in Figure 16; Controller 1640 is from temperature transducer 1638 receiver gases mixture temperature signals 1630, and temperature transducer 1638 detects the temperature of the gaseous mixture that mixes with thermal exhaust by 1616 generations of catalytic type diesel particulate filter from the cooling air of compressor 1608 supplies.In addition, controller 1640 detects the compressed air inlet pressure signal 1632 that is produced by pressure transducer 1636, and pressure transducer 1636 is arranged in from the compressed-air actuated conduit of compressor 1608 supplies.In addition, the engine speed signal 1626 from motor 1602 or throttle valve supply is supplied to controller 1640 with engine loading signal 1628.

About at a high speed, high load condition controls the temperature of the gaseous mixture that is supplied to turbine 1606 down, controller 1640 is the temperature of temperature limitation to the operation that maximizes turbine 1606 of gaseous mixture, and can the high mechanism that must damage turbine 1606.In one embodiment, the temperature of about 925 ° of C is the optimum temperature of gaseous mixture operation turbine 1606.Begin to surpass 900 ° of C in case be supplied to the temperature of the gaseous mixture of turbine 1606, feedback valve 1618 is opened to allow and before the pressurized air of compressor 1608 is penetrating turbine 1606, is cooled off the thermal exhaust from catalytic type diesel particulate filter 1616 so.The temperature that controller 1640 can be designed to about 925 ° of C is a target, and the upper bound is limited to 950 ° of C and lower bound is limited to 900 ° of C.The limiting value of 950 ° of C is to use traditional material that the temperature to the damage of turbine 1606 possibly take place.Certainly, depend on the assembly of use in the turbine 1606 and the Special Category of material, said controller can be designed to other temperature.Can use conventional proportional-integral-derivative (PID) control logic device to produce these controlled results in the controller 1640.

The benefit of the temperature of the gaseous mixture of control entering turbine 1606 is to eliminate uses fuel to limit the turbine-entry temperature of gaseous mixture in exhaust.Use needs a large amount of air than the thermal exhaust that the cold compression air stream cools off from catalytic type diesel particulate filter 1616, and this comprises the required colder temperature that big quality reaches gaseous mixture.Cooling is very big from the required air quantity of the thermal exhaust of catalytic type diesel particulate filter 1616, this be because from compressor 1608 be not good freezing mixture than the cold compression air, when especially comparing with the liquid fuel that injects exhaust.Thermal exhaust from the output terminal of catalytic type diesel particulate filter 1616 causes expanding to produce gaseous mixture than cold compression gas from compressor 1608.Since from the big quality of compressor 1608 need reduce temperature than the cold compression air from the thermal exhaust of catalytic type diesel particulate filter 1616, so the gas mixture streams of big quality flows through turbine 1606, this has improved the output of turbine 1606 greatly.Turbo-power reason mass flow deducts compressive flow and crosses the differential force that the differential of the required merit of the pressurized air of feedback valve 1618 produces and improve.Through obtaining temperature of gas mixture signal 1630 from temperature transducer 1638 and, just can not surpassing maximum temperature through the compressed-air actuated interpolation of feedback valve 1618 controls.

Controller 1640 also Control and Feedback valve 1618 comes the surge in the limit compression device 1608.Surge limit is along with the boundary of boosting, the design of air stream through compressor and compressor 1608 changes.When intake air 1622 stream when being high for the pressure ratio between low and intake air 1622 and the pressurized air, normally used compressor in the turbosupercharger (for example compressor 1608) surpasses surge limit.In the super turbosupercharger of tradition, when engine speed (rpm) 1626 when low, intake air 1622 streams are for low.Under low rpm, when motor 1602 did not use pressurized air in a large number, the mass flow of intake air 1622 was for low and because rotary compressor 1608 can't be under the situation that no rational intake air 1622 flows be pushed into air surge takes place in the high-pressure conduit.Feedback valve 1618 is allowed the stream that passes air-pressure duct 1609 and is prevented or reduce the surge in the compressor 1608.In case in the compressor 1608 surge takes place, can't keep the pressure in the air-pressure duct 1609 so.Therefore, under the low rpm of motor 1602, high capacity serviceability, the compressed-air actuated pressure in the air-pressure duct 1609 can be reduced to desired level down.Through opening feedback valve 1618, increase intake air 1622 streams that pass compressor 1608, especially under the low rpm of motor 1602, high capacity serviceability, this allows and in air-pressure duct 1609, reaches required boost level.Feedback valve 1618 can be opened simply reaches required pressure in air-pressure duct 1609.Yet, through detecting boosting in the air-pressure duct 1609 simply, make compressor 1608 avoid before the surging condition surge taking place opening feedback valve 1618.

Yet, preferably before the generation surging condition, measure surge limit and open feedback valve 1618 in advance.For given rpm and required boost level, can measure surge limit.Feedback valve 1618 can begin to open before compressor 1608 reaches the calculating surge limit.Previously open said valve and allow that compressor upwards rotates to higher boosting quickly, this is because said compressor more approaches the greater efficiency point of compressor operation parameter.Then can realize low rpm boosting fast of rising down.Through taking place to open said valve before the surge, can also realize more stable control system.

Realize through allowing that motor 1602 reaches higher boosting more quickly when motor 1602 is in low rpm when opening feedback valve 1618 with a kind of mode of response of feasible improvement motor 1602.Compressor 1608 is also more effective, and this causes the less merit of gearbox 1610 usefulness to realize super supercharging.Surge limit control can be molded in the mode standard based on the control simulation code, for example MATLAB.The autocoding of the algorithm of the molded by this way simulation that will allow controller 1640 and controller 1640.

Pattern based on control system described above is unique because use rotation that gearbox 1610 controls turbine 1606 with compressor 1608 generations boost and do not have turbo.In other words, gearbox 1610 can extract that energy of rotations come drive compression device 1608 and very fast and produce enough mechanical energy at turbine 1606 and come to boost air-pressure duct 1609, to reach required before this desired level drive compression device 108 from arbor 1612.In this way, reduce or eliminate the control piece that reduces sluggishness in the conventional turbine pressurized machine.Should be designed in the operating parameter that the optimum efficiency that makes compressor 1608 remains on compressor 108 based on the pattern of the control of controller 1640.

The control mode of controller 1640 is molding pressure operating parameter carefully also, and it is plotted as the mass flow that the motor that contrasts given target velocity that wherein target velocity and load can define with respect to the position of throttle valve for automobiles and load is allowed.As shown in Figure 16, engine speed signal 1626 can obtain and be applied to controller 1640 from motor 1602.Similarly, engine loading signal 1628 can obtain and be applied to controller 1640 from motor 1602.Perhaps, these parameters can obtain from the sensor that is positioned on the engine throttle (not shown).Then, feedback valve 1618 can respond the control signal 1642 that is produced by controller 1640 and operate.Pressure transducer 1636 produces the compressed air inlet pressure signal 1632 that is applied to controller 1640, and controller 1640 responding engine rate signals 1626, engine loading signal 1628 and compressed air inlet pressure signal 1632 come compute control signal 1642.

During the serviceability of motor 1602; Wherein compressor 1608 keep off surge limit and as do not reach the temperature of gaseous mixture by 1638 detections of temperature transducer, the system when feedback valve 1618 is closed comes work as the super turbo charged system of tradition.This occurs on most of operating parameter of motor 1602.When high capacity that motor 1602 takes place and low rpm state, feedback valve 1618 is opened and is prevented surge.Similarly; Under the high rpm of motor 1602, high capacity serviceability; In the exhaust of the output terminal of catalytic type diesel particulate filter 1616, produce high temperature, so feedback valve 1618 must be opened the temperature that makes the fuel mixture that is applied to turbine 1606 and is reduced to and is lower than the temperature that can cause damage to turbine 1606.

Figure 17 is the detail drawing of the embodiment of the efficient super turbo charged engine system 1600 shown in Figure 16.As shown in Figure 17; Motor 1602 comprise such as preceding text about Figure 16 the super turbosupercharger that has been modified of description provide than the higher total efficiency of the super turbo charged motor of tradition, and height, optimum efficiency and the high rpm in low rpm, the high capacity serviceability, height, the optimum efficiency under the high load condition are provided.Super turbosupercharger comprise by shaft mechanical be connected to the turbine 1606 of compressor 1608.Compressor 1608 compresses intake airs 1622 and will compress inlet air supply to conduit 1704.Conduit 1704 is connected to feedback valve 1618 and interstage cooler 1614.Disclosed like preceding text, interstage cooler 1614 is used for cooling off the pressurized air of heating during compression process.Interstage cooler 1614 is connected to air-pressure duct 1726, and air-pressure duct 1726 then is connected to the inlet manifold (not shown) of motor 1602.Pressure transducer 1636 is connected to air-pressure duct 1704 and comes detected pressures and the compressed air pressure signal 1632 supply pressure readings through being applied to controller 1640.Disclosed like preceding text, feedback valve 1618 is controlled by the controller feedback valve control signal 1642 that is produced by controller 1640.Under some serviceability, feedback valve 1618 is opened pressurized air is supplied to mixing chamber 1706 from air-pressure duct 1704.

Shown in the embodiment of Figure 17; Mixing chamber 1706 comprises a series of openings 1702 in the catalytic type diesel particulate filter output duct 1708 that is surrounded by air-pressure duct 1704 simply, makes that passing opening 1702 from the pressurized air of air-pressure duct 1704 supplies mixes with exhaust the catalytic type diesel particulate filter output duct 1708.Can use the mixing chamber of any required kind to mix and reduce the temperature of said exhaust than cold compression air and exhaust.Temperature transducer 1638 is arranged in catalytic type diesel particulate filter output duct 1708.Temperature transducer 1638 supply gas mixture temperature signals 1630 are to controller 1640, and controller 1640 Control and Feedback valves 1618 guarantee that the temperature of the exhaust in the catalytic type diesel particulate filter output duct 208 is no more than the maximum temperature that can cause damage to turbine 1606.Catalytic type diesel particulate filter 1616 is connected to gas exhaust manifold 1710 through catalytic type diesel particulate filter entry conductor 1714.Through catalytic type diesel particulate filter 1616 is orientated as near gas exhaust manifold 1710, be flowed directly in the catalytic type diesel particulate filter 1616 from the thermal exhaust of motor, this helps to start catalytic type diesel particulate filter 1616.In other words; Catalytic type diesel particulate filter 1616 is not allowed said exhaust cooling in fact before getting into catalytic type diesel particulate filter 1616 near the proximal most position of the outlet of engine exhaust, and this has improved the performance of catalytic type diesel particulate filter 1616.When catalytic type diesel particulate filter 1616 was passed in said exhaust, catalytic type diesel particulate filter 1616 was that said exhaust increases additional heat.The exhaust that these of the output terminal of catalytic type diesel particulate filter 1616 are very warm is provided to catalytic type diesel particulate filter output duct 208 and in mixing chamber 1706, uses the compression inlet air cooling from air-pressure duct 1704.The temperature that depends on the very hot exhaust that produces at the output terminal of catalytic type diesel particulate filter 1616; Its serviceability according to motor 1602 changes, and the compression intake airs of different amounts will be added in the said exhaust during high speed, high load condition.During low engine speed, engine high load state, feedback valve 1618 is also in order to allow that intake air flows through compressor and avoids surge.Surge is similar to the aerodynamic force stall of compressor blade, and this is owing to the low stream mode of during the low engine speed state, passing compressor takes place.But when surge took place, the pressure in the inlet manifold (not shown) descended, and this is because compressor 1608 can't compress intake air.Through allowing air stream overcompression device 1608 owing to open feedback valve 1618, can keep the pressure in the inlet manifold, make that said high moment of torsion can be achieved owing to high inlet manifold pressure when under low engine speed, needing high moment of torsion.

Disclosed like preceding text, when motor was operated under high speed, high load condition, catalytic type diesel particulate filter 1616 caused and produces a large amount of heats in the exhaust that is provided to catalytic type diesel particulate filter output duct 1708.Through supplied with compressed, colder intake air to catalytic type diesel particulate filter output duct 1708, at a high speed, the thermal exhaust under the high load condition is cooled.When the load of motor and speed improve, produce hotter gas and the air that need contract from the more multiple pressure of conduit 1704.If turbine 1606 does not provide enough energy of rotations to come the drive compression device; Such as under low speed, high load condition, engine crankshaft 1612 can be passed through rotating band 1722, drive pulley 1718, axle 1724, continuous variable gearbox 1716 and gearbox 1728 supply energy of rotation to compressors 1608 so.Moreover, can use to advance any part of system to supply energy of rotation to compressor 1608, and Figure 17 openly carries into execution a plan according to one of an open embodiment.

Equally as shown in Figure 17, cold start-up valve 1620 also is connected to air-pressure duct 1704, and then air-pressure duct 1704 is connected to cold start-up conduit 1712.Cold start-up conduit 1712 is connected to the catalytic type diesel particulate filter entry conductor 1714 at catalytic type diesel particulate filter 1616 upper reaches.Disclosed like preceding text, the purpose of cold start-up valve is the input end that compression intake air to catalytic type diesel particulate filter 1616 is provided under starting state.Under starting state, before catalytic type diesel particulate filter 1616 reaches the full operation temperature, provide extra oxygen to begin catalytic process through cold start-up conduit 1712.The said extra oxygen that provides through cold start-up conduit 1712 helps the beginning of catalytic process.Controller 1640 responding engine rate signals 1626, engine loading signal 1628 and temperature of gas mixture signal 1630 are controlled cold start-up valve 1620 through controller cold start-up valve control signal 1644.

Therefore, efficient, super turbo charged motor 1600 is operated with the mode that is similar to super turbosupercharger, except feedback valve 1618 owing to two reasons are supplied to a compressed-air actuated part the input end of turbine from compressor.Reason is before exhaust gets into turbine, to cool off said exhaust to make at a high speed, can use whole energy of said exhaust and not need the waste gas gate under the high load condition.Another reason provides the air stream that passes compressor and prevents the surge under low rpm, the high load condition.In addition; Before exhaust arrives turbine; The catalytic type diesel particulate filter can be connected in the blast air; Make the heat that is produced by catalytic type diesel particulate filter 1616 can be used for driving turbine 1606, and make the compression that mixes with hot gas from catalytic type diesel particulate filter 1616 air expansion that enters the mouth, this has improved the efficient of system greatly.In addition, cold start-up valve 1620 can be used for through during starting state, providing oxygen to exhaust to begin the catalytic process in the catalytic type diesel particulate filter 1616.

Therefore; Disclose the unique super turbosupercharger of high speed traction-driven that a kind of use has fixed ratio, said fixed ratio is reduced to the rpm level that can be used by the continuous variable gearbox of coupling energy between propelling system and turbine/compressor axle with the rotating machinery speed of turbine/compressor axle.The uniqueness of said super turbocharger design is that gearbox is arranged in the system.Said continuous variable gearbox is arranged in the bottom of super turbosupercharger shell.Continuous variable gearbox 1116 is provided at and transmits the required stepless variable velocity ratio of rotating mechanical energy between super turbosupercharger and the motor.Arbitrary gear continuous variable gearbox can be used as continuous variable gearbox 1116 maybe can use traction-driven continuous variable gearbox.Therefore, traction drive can be used for high speed traction drive 114 and continuous variable gearbox 1116 both.

Be that explanation and purpose of description present aforementioned description of the present invention.Be not to be intended to detailed or the present invention is restricted to disclosed accurate form, and other modifications and change can be arranged according to above-mentioned teaching.Embodiment is to select in order to explain best that principle of the present invention and its practical are used and describe, and can let others skilled in the art use the present invention best with the various embodiments and the various modification of the specific use that is suitable for expecting thus.The claim of enclosing is intended to be interpreted as except being subject to the scope of prior art, also comprises other alternate embodiment of the present invention.

Claims

1. super turbosupercharger that is coupled to motor, it comprises:

Turbine, it produces the turbine rotating mechanical energy by the exhaust enthalpy through said engine producing;

Compressor, its compression suck air and response is supplied to said motor by the said turbine rotating mechanical energy of said turbine generation and the engine revolution mechanical energy that transmits from said motor with pressurized air;

Axle, it has the end that is connected to said turbine and said compressor, and the central part with traction surface;

Traction drive, it is arranged in around the said central part of said axle, and said traction drive comprises:

A plurality of planet rolling barrels, it has a plurality of planet rolling barrel traction surface, and said planet rolling barrel traction surface and said axle traction surface circle connect and make and have a plurality of first traction interface between said a plurality of planet rolling barrel traction surface and the said traction surface;

The annular cylinder, it is rotated through a plurality of second traction interface by said a plurality of planet rolling barrels;

The continuous variable gearbox; It mechanically is coupled to said traction drive and said motor, and it is sent to the turbine rotating mechanical energy said motor and under the service speed of said motor, engine revolution mechanical energy is sent to said super turbosupercharger.

2. super turbosupercharger according to claim 1, wherein said continuous variable gearbox comprises traction-driven continuous variable gearbox.

3. super turbosupercharger according to claim 2, wherein said continuous variable gearbox comprise planet ball bearing traction-driven continuous variable gearbox.

4. super turbosupercharger according to claim 2, wherein said traction drive comprise the planet traction drive with at least two planet rolling barrels.

5. super turbosupercharger according to claim 4, wherein said planet traction drive has at least three planet rolling barrels.

6. super turbosupercharger according to claim 4, wherein said planet traction drive has the planet carrier that said planet rolling barrel is installed on it.

7. super turbosupercharger according to claim 6, wherein said planet traction drive has the multipath planet rolling barrel.

8. super turbosupercharger according to claim 6, wherein said annular cylinder has annular cylinder traction surface, and said annular cylinder traction surface and said a plurality of planet rolling barrel traction surface circle connect to set up said a plurality of second traction interface.

9. super turbosupercharger according to claim 7, wherein said annular cylinder have with diameter and fetch the annular cylinder traction surface of setting up said a plurality of second traction interface less than a plurality of extra planet rolling barrel traction surface circle of said a plurality of planet rolling barrel traction surface.

10. method that between super turbosupercharger and motor, transmits rotating mechanical energy, it comprises:

Exhaust enthalpy by through said engine producing produces the turbine rotating mechanical energy in turbine;

Using compressor compresses to suck air responds the said turbine rotating mechanical energy that produced by said turbine and by the engine revolution mechanical energy of said engine producing pressurized air is supplied to said motor;

Axle is provided, and it has the end that is connected to said turbine and said compressor, and the central part with traction surface;

Traction drive mechanically is coupled to the said axle traction surface of said axle;

A plurality of planet rolling barrel traction surface of placing a plurality of planet rolling barrels make the said axle of its contact traction surface and between said a plurality of planet rolling barrel traction surface and said axle traction surface, set up a plurality of first traction interface;

Placing annular cylinder makes it contact said a plurality of planet rolling barrel to make and between said a plurality of planet rolling barrels and said annular cylinder, set up a plurality of second traction interface;

The continuous variable gearbox mechanically is coupled to said traction drive and said motor and under the service speed of said motor said turbine rotating mechanical energy is being sent to said motor and under the service speed of said compressor and said turbine, engine revolution mechanical energy is being sent to said axle.

11. comprising through at least one mechanical device, method according to claim 10, the said process that wherein between said super turbosupercharger and said motor, transmits rotating mechanical energy transmit rotating mechanical energy.

12. method according to claim 11, wherein the said process through at least one mechanical device transmission rotating mechanical energy comprises that the gearbox through vehicle transmits rotating mechanical energy.

13. method according to claim 11, wherein the said process through at least one mechanical device transmission rotating mechanical energy comprises the propelling system that transmits rotating mechanical energy to vehicle.

14. method according to claim 10 is wherein placed said annular cylinder its said process that contacts said a plurality of planet rolling barrels is comprised:

The annular cylinder traction surface of placing said annular cylinder makes it contact said a plurality of planet rolling barrel traction surface and sets up said a plurality of second traction interface.

15. method according to claim 10 is wherein placed said annular cylinder its said process that contacts said a plurality of planet rolling barrels is comprised:

The annular cylinder traction surface of placing said annular cylinder makes its contact diameter set up said a plurality of second traction interface less than a plurality of extra planet rolling barrel traction surface of said a plurality of planet rolling barrel traction surface.

16. method according to claim 10 wherein mechanically is coupled to the said process of said traction-driven with the continuous variable gearbox and comprises:

Traction-driven continuous variable gearbox mechanically is coupled to said traction drive.

17. method according to claim 16 wherein mechanically is coupled to the said process of said traction-driven with traction-driven continuous variable gearbox and comprises:

The continuous variable gearbox of planet ball bearing mechanically is coupled to said traction drive.

18. method according to claim 16 wherein comprises the said process that traction drive mechanically is coupled to said axle traction surface:

Mechanically coupling has the planet traction drive of at least three multipath planet rolling barrels.

19. a method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, it comprises:

The high-pressure exhaust of first preliminary dimension is provided in said internal-combustion engine;

The low pressure exhaust mouth of second preliminary dimension is provided in said internal-combustion engine, and said second preliminary dimension is in fact greater than said first preliminary dimension;

Use the driving high-voltage super turbosupercharger of first portion at least from the high pressure gas of said high-pressure exhaust;

To the inlet manifold to said internal-combustion engine be provided from the second portion at least of the said high pressure gas of said high-pressure exhaust;

Use low pressure exhaust to drive the super turbosupercharger of low pressure from said low pressure exhaust mouth;

To the air input end to said high pressure compressor be provided from the pressurized air of the output terminal of said low pressure compressor;

Under predetermined pressure, will the inlet manifold to said internal-combustion engine be provided from the pressurized air of the output terminal of said high pressure compressor;

Opening said high-pressure exhaust when the pressure in the said high-pressure exhaust during greater than said predetermined pressure makes the said second portion of said high pressure gas connect said internal-combustion engine recirculation.

20. method according to claim 19, it also comprises:

Use valve to control the said amount of the said second portion of said high pressure gas with respect to the said first portion of said high pressure gas, the said second portion that said valve is arranged in said high pressure gas provides to the conduit of said inlet manifold.

21. a method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, it comprises:

Use high pressure gas to drive the high-voltage super turbosupercharger from said high-pressure exhaust;

To guide to the inlet manifold of said internal-combustion engine from the said high pressure gas of the output terminal of said high-voltage super turbosupercharger;

Opening said high-pressure exhaust during greater than said predetermined pressure when the pressure in the said high-pressure exhaust makes the said high pressure gas from the said output terminal of said high-voltage super turbosupercharger connect said internal-combustion engine recirculation.

22. method according to claim 21, it also comprises:

To provide from the part of the said high pressure gas of the said output terminal of said high-voltage super turbosupercharger to said low pressure exhaust and assist to drive the super turbosupercharger of said low pressure.

23. a method that is beneficial to the exhaust gas recirculatioon in the super turbo charged internal-combustion engine, it comprises:

To provide from the high pressure gas of said high-pressure exhaust to the inlet manifold of said internal-combustion engine;

Under predetermined pressure, will the inlet manifold to said internal-combustion engine be provided from the pressurized air of the output terminal of said low pressure compressor;

24. method according to claim 23, it also comprises:

The part of said high pressure gas provided to said low pressure exhaust assist to drive the super turbosupercharger of said low pressure.

25. a method of improving the efficient of super turbo charged engine system, it comprises:

Motor is provided;

The catalytic type diesel particulate filter is provided; It is connected to the relief opening that receives engine exhaust near said motor from said motor; Said engine exhaust activates the exothermic reaction in the said catalytic type diesel particulate filter, and said exothermic reaction is that said engine exhaust increases extra energy and produces the catalytic type exhaust hotter than said engine exhaust at the output terminal of said catalytic type diesel particulate filter;

Use compressor to provide pressurized air to flow to the inlet of said motor;

In the mixing chamber that is in said catalytic type diesel particulate filter downstream, a said compressed-air actuated part mixed with said catalytic type exhaust and produce said catalytic type exhaust and said compressed-air actuated gaseous mixture;

Use control valve to regulate the said compressed-air actuated said stream that gets into said mixing chamber and make said gaseous mixture keep below maximum temperature, and during the phase of operation of said motor when in the said compressor otherwise make the maintenance of said pressurized air stream pass said compressor can surge take place the time;

Respond said gas mixture streams and said gaseous mixture is supplied to the turbine that produces the turbine rotating mechanical energy;

Said turbine rotating mechanical energy is transferred to said compressor from said turbine; When the said stream of the said gaseous mixture that passes said turbine was enough to drive said compressor, said compressor used said turbine rotating mechanical energy source of compressed air to produce said pressurized air;

Extract at least a portion of said turbine rotating mechanical energy and in the time need not making said compressor operation, the said part of said turbine rotating mechanical energy is applied to from said turbine and advance system from the said part of the said turbine rotating mechanical energy of said turbine;

When the said stream of the said gaseous mixture that passes said turbine is not enough to drive said compressor, will be that rotating mechanical energy provides to said compressor and prevents turbo from the propelling of said propelling system.

, method according to claim 25, the said maximum temperature of wherein said gaseous mixture can cause the temperature of damage to said turbine 26. being lower than said gaseous mixture.

27. method according to claim 26, the said maximum temperature of wherein said gaseous mixture are lower than about 950 ℃.

28. method according to claim 26, the said efficient of wherein said motor is able to improve through the too much gas that does not use the waste gas valve to discharge said gaseous mixture.

29. method according to claim 28 is wherein extracted too much turbine rotating mechanical energy and will will be that rotating mechanical energy provides to the said process of said compressor and comprises from the propelling of said propelling system from said turbine:

Use said propelling system with is connected said turbine and said compressor spool between be coupled said too much turbine rotating mechanical energy and said propelling be the gearbox of rotating mechanical energy.

30. method according to claim 29, the said process of wherein during the phase of operation of said motor, keeping said pressurized air stream comprises:

When the operation of said low engine speed and when needing high moment of torsion, reduce surge and make said pressurized air stream keep passing said compressor through opening said feedback valve.

31. method according to claim 30, the said process of wherein in mixing chamber, mixing said pressurized air and said catalytic type exhaust comprises:

In being connected to the exhaust manifolds of air-pressure duct, provide at least one opening to make said pressurized air flow through said at least one opening and mix with said hotter exhaust in the said exhaust manifolds.

32. method according to claim 31, it also comprises:

During the cold start-up of said motor, mixing a said compressed-air actuated part provides oxygen to said catalytic type diesel particulate filter with the said exhaust that is in the said catalytic type diesel particulate filter upper reaches, and this helps said catalyzing type purifier to begin said exothermic reaction.

33. a super turbo charged engine system, it comprises:

Motor;

The catalytic type diesel particulate filter; It is connected near the feasible thermal exhaust from said motor of the exhaust manifolds of said exhaust opening of engine and activates the exothermic reaction in the said catalytic type diesel particulate filter, and said exothermic reaction is that said thermal exhaust increases energy and produces the catalytic type exhaust;

Compressor, it is connected to provides compressed-air actuated air source, and said pressurized air has the pressure greater than the stress level of said exhaust;

Conduit, it is supplied to said catalytic type exhaust with said pressurized air and makes said compressed-air actuated at least a portion mix with said catalytic type exhaust to produce gaseous mixture;

Turbine, it mechanically is coupled to said compressor and produces the turbine rotating mechanical energy by said gaseous mixture;

Valve; The said compressed-air actuated said part that said conduit is passed in its adjusting flows and makes said gaseous mixture keep below predetermined maximum temp, and during the phase of operation of said motor when in the said compressor otherwise make air stream keep passing said compressor can surge take place the time from said air source;

Gearbox, when the said stream of the said exhaust of passing said turbine was not enough to optionally drive said compressor, the propelling of the system of self-propelled in the future was that rotating mechanical energy provides to said compressor and reduces turbo ...