CN102822471B

CN102822471B - There is the super-turbocharger of high speed traction driving and continuous variable gearbox

Info

Publication number: CN102822471B
Application number: CN201080065828.5A
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: 2015-12-16
Anticipated expiration: 2030-02-05
Also published as: DE112010005233B4; AU2010345054A1; ES2453204R1; ES2453204B1; SE1250994A1; JP5688417B2; JP2013519034A; GB2489647A; MX356972B; WO2011096936A1; GB2489647B; ES2453204A2; CN102822471A; AU2010345054B2; MX2012009009A; DE112010005233T5; GB201214265D0; CA2786580A1

Abstract

The invention provides a kind of super-turbocharger, its use is coupled to the high speed of continuous variable gearbox, the traction drive of fixed ratio to allow high speed operation.High speed traction drives to be used to provide and slows down from the speed of high-speed turbine axle.Second traction drive provides the velocity ratio of stepless variable by continuous variable gearbox.Also disclose the gas recirculation in super-turbocharger.

Description

There is the super-turbocharger of high speed traction driving 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, the partial continuous case of 421, the U.S. Provisional Patent Application No.61/086 of described application requirement application on August 5th, 2008, the right of 401, whole teaching of described application and disclosure are incorporated herein by reference.

Background of invention

Traditional turbosupercharger is by used heat and exhaust gas driven, and it is forced to through exhaust driven gas turbine shell on turbine.Turbine is connected to compressor wheel by common turbine shaft.When turbine is encountered in exhaust, two wheels rotate simultaneously.The compressor shell that is rotated through of compressor wheel sucks air, and it forces pressurized air to enter engine cylinder to realize the engine performance and fuel efficiency improved.Size for the turbosupercharger of speed change/variable load application is applicable to the maximal efficiency under torque peak speed usually to produce enough boostings reaching Peak torque.But at lower speeds, turbosupercharger produces insufficient boosting and responds for suitable motor instant.

In order to overcome these problems and provide the system increasing efficiency, super-turbocharger can be used, the feature of described super-turbocharger combining super pressurized machine and turbosupercharger.Super-turbocharger is incorporated to the super pressurized machine mainly containing and benefit low speed and large torque and the benefit being usually only of value to the turbosupercharger of high speed high pass filter.Super-turbocharger in conjunction with turbosupercharger with Engine torque can be positioned over gearbox turbine shaft being used for super supercharging and eliminating turbo lag.More work once exhaust energy starts to provide than driving compressor, so super-turbocharger regains excessive power by applying excess power to piston engine (usually passing through arbor).Therefore, super-turbocharger provides value-added two benefits of low speed and large torque and high speed high pass filter completely from a system.

Brief summary of the invention

Therefore, embodiment of the present invention can comprise the super-turbocharger being coupled to motor, and it comprises: turbine, and it produces turbine rotating mechanical energy by the exhaust enthalpy produced by described motor; Compressor, its compression sucks air and responds the described turbine rotating mechanical energy that produced by described turbine and from the engine revolution mechanical energy that described motor transmits, pressurized air be supplied to described motor; Axle, it has the end being connected to described turbine and described compressor, and has the central part of axle traction surface; Traction drive, it is arranged in around the described central part of described axle, described traction drive comprises: multiple planet rolling barrel, it has multiple planet rolling barrel traction surface, and described planet rolling barrel traction surface and described axle traction surface circle connect and make to there is multiple first traction interface between described multiple planet rolling barrel traction surface and described axle traction surface; Circular-cylindrical, it is rotated by multiple second traction interface by described multiple planet rolling barrel; Continuous variable gearbox, it is mechanically coupled to described traction drive and described motor, and turbine rotating mechanical energy is sent to described motor and under the service speed of described motor, engine revolution mechanical energy is sent to described super-turbocharger by it.

Embodiment of the present invention can also comprise a kind of method transmitting rotating mechanical energy between super-turbocharger and motor, and it comprises: in turbine, produce turbine rotating mechanical energy by the exhaust enthalpy produced by described motor; Compression suction air responds the described turbine rotating mechanical energy produced by described turbine and pressurized air is supplied to described motor by the engine revolution mechanical energy produced by described motor; There is provided axle, it has the end being connected to described turbine and described compressor, and has the central part of axle traction surface; Traction drive is mechanically coupled to the described axle traction surface of described axle; Multiple planet rolling barrel traction surface of placing multiple planet rolling barrel make it contact described axle traction surface to make to set up multiple first traction interface between described multiple planet rolling barrel traction surface and described axle traction surface; Place circular-cylindrical to make it contact described multiple planet rolling barrel to make to set up multiple second traction interface between described multiple planet rolling barrel and described circular-cylindrical; Continuous variable gearbox be mechanically coupled to described traction drive and described motor and described turbine rotating mechanical energy be sent to described motor and under the service speed of described motor, engine revolution mechanical energy be sent to described super-turbocharger.

Embodiment of the present invention can also comprise a kind of method of the exhaust gas recirculatioon be beneficial in super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust providing the first preliminary dimension in described internal-combustion engine; In described internal-combustion engine, provide the low pressure exhaust mouth of the second preliminary dimension, described second preliminary dimension is greater than in fact described first preliminary dimension; High-voltage super turbosupercharger is driven with at least first portion of the high pressure gas from described high-pressure exhaust; At least second portion of the described high pressure gas from described high-pressure exhaust is provided to the inlet manifold of described internal-combustion engine; Low pressure super-turbocharger is driven with the low pressure exhaust from described low pressure exhaust mouth; The pressurized air of the output terminal from described low pressure compressor is provided to the air input of described high pressure compressor; Under a predetermined, the pressurized air of the output terminal from described high pressure compressor is provided to the inlet manifold of described internal-combustion engine; Open described high-pressure exhaust when the pressure in described high-pressure exhaust is greater than described predetermined pressure and make the through described internal-combustion engine recirculation of the described second portion of described high pressure gas.

Embodiment of the present invention can also comprise a kind of method of the exhaust gas recirculatioon be beneficial in super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust providing the first preliminary dimension in described internal-combustion engine; In described internal-combustion engine, provide the low pressure exhaust mouth of the second preliminary dimension, described second preliminary dimension is greater than in fact described first preliminary dimension; High-voltage super turbosupercharger is driven with the high pressure gas from described high-pressure exhaust; Low pressure super-turbocharger is driven with the low pressure exhaust from described low pressure exhaust mouth; The pressurized air of the output terminal from described low pressure compressor is provided to the air input of described high pressure compressor; Under a predetermined, the pressurized air of the output terminal from described high pressure compressor is provided to the inlet manifold of described internal-combustion engine; The described high pressure gas of the output terminal from described high-voltage super turbosupercharger is guided to the inlet manifold of described internal-combustion engine; The through described internal-combustion engine recirculation of described high pressure gas that described high-pressure exhaust makes from the described output terminal of described high-voltage super turbosupercharger is opened when the pressure in described high-pressure exhaust is greater than described predetermined pressure.

Embodiment of the present invention can also comprise a kind of method of the exhaust gas recirculatioon be beneficial in super turbo charged internal-combustion engine, and it comprises: the high-pressure exhaust providing the first preliminary dimension in described internal-combustion engine; In described internal-combustion engine, provide the low pressure exhaust mouth of the second preliminary dimension, described second preliminary dimension is greater than in fact described first preliminary dimension; High pressure gas from described high-pressure exhaust is provided to the inlet manifold of described internal-combustion engine; Low pressure super-turbocharger is driven with the low pressure exhaust from described low pressure exhaust mouth; Under a predetermined, the pressurized air of the output terminal from described high pressure compressor is provided to the inlet manifold of described internal-combustion engine; Open described high-pressure exhaust when the pressure in described high-pressure exhaust is greater than described predetermined pressure and make the through described internal-combustion engine recirculation of the described second portion of described high pressure gas.

Accompanying drawing is sketched

Fig. 1 is the side view of the embodiment of super-turbocharger.

Fig. 2 is the large figure such as the perspective of the embodiment of the super-turbocharger of Fig. 1.

Fig. 3 A is the side perspective of the embodiment of illustrated super-turbocharger in Fig. 1 and Fig. 2.

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

Fig. 3 C is the side perspective of the modification of the embodiment of illustrated super-turbocharger in Fig. 1, Fig. 2 and Fig. 3 A.

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

Figure 10 is the diagram of another embodiment that high speed traction drives.

Figure 11 and Figure 12 is the diagram of the embodiment of traction continuously variable gearbox.

Figure 13 is the side cutaway view of another embodiment.

Figure 14 A is the schematic diagram of the embodiment of super turbo charged gas recirculation device.

Figure 14 B is the schematic diagram of another embodiment of super turbo charged gas recirculation device.

Figure 14 C is the schematic diagram of another embodiment of super turbo charged gas recirculation device.

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

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

Figure 15 is the diagram of simulation BSFC improvement project.

Embodiment

Fig. 1 is the schematic diagram of the embodiment of the super-turbocharger 100 using high speed traction driving 114 and continuous variable gearbox 116.As shown in fig. 1, super-turbocharger 100 is coupled to motor 101.Described super-turbocharger comprises turbine 102, and described turbine 102 is coupled to motor 101 by exhaust manifolds 104.Turbine 102 receives thermal exhaust from exhaust manifolds 104 and produce rotating mechanical energy before discharge exhaust relief opening 112.Catalytic type diesel particulate filter (not shown) can be connected between exhaust manifolds 104 and turbine 102.Or described catalytic type diesel particulate filter (not shown) can be connected to relief opening 112.The rotating machinery produced by turbine 102 is transferred into compressor 106 by turbine/compressor axle (axle 414 of such as Fig. 4), rotate the compressor fan be arranged in compressor 106, its compressed air inlet 110 and by compressed air delivery to conduit 108, conduit 108 is coupled to the inlet manifold (not shown) of motor 101.Disclosed in above application reference, be different from turbosupercharger, super-turbocharger is coupled to and advances system to transmit its energy to described propelling system or to transmit energy from described propelling system.Advance system can comprise motor 101 as referred to herein, be furnished with the speed changer of the vehicle of motor 101, be furnished with the drivetrain of the vehicle of motor 101 or other application of the rotating mechanical energy that produced by motor 101.In other words, rotating mechanical energy by least one intermediate mechanical device (speed changer of such as vehicle or drivetrain) coupling or can be sent to motor from super-turbocharger, and vice versa.In the implementation of figure 1, the rotating machinery of super-turbocharger couples directly to the arbor 122 of motor 101 by axle 118, pulley 120 and line belt 124.Equally as shown in fig. 1, high speed traction drives 114 to be mechanically coupled to continuous variable gearbox 116.

In operation, the high speed traction of Fig. 1 drives 114 to be mechanically be coupled to turbine/compressor axle fixed ratio, high speed traction driving, uses traction interface rotating mechanical energy to be sent to turbine/compressor axle or transmits rotating mechanical energy from turbine/compressor axle.High speed traction drives 114 to have fixed ratio, and they can be different according to motor 101.For mini engine, high speed traction is needed to drive the large fixed ratio of 114.

For less motor, the compressor of super-turbocharger and turbine littlely must keep mini engine size and mate the flow demand of compressor and turbine.In order to make less turbine and less compressor suitably play a role, it must rotate with higher rmp.For example, less motor may need compressor and turbine to rotate with 300,000rpm.For minimum motor (such as half liter of motor), super-turbocharger may need to rotate with 900,000rpm.It is avoid surge that less motor needs with a reason of the compressor of higher rpm levels operation.In addition, in order to operate in an efficient way, the head velocity of compressor just in time must not reach velocity of sound.Because described top is not as the length in less compressor, so the top of compressor less under identical rpm is not as moving soon in the top of larger compressor.When the size of compressor reduces, the rotational speed exponential type needed for valid function rises.Because gear is limited to about 100,000rpm, so the power that the gear train of standard consumes under cannot being used for reaching the fair speed needed for motor car engine super-turbocharger.Therefore, various embodiment uses high speed traction to drive 114 to increase power and from turbine shaft received power.

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

The embodiment being suitable for use as the continuous variable gearbox of the gearbox of continuous variable disclosed in Fig. 1 116 is the gearbox of continuous variable disclosed in Figure 11 and Figure 12.Other embodiment that can be used as the continuous variable gearbox of the continuous variable gearbox 116 of Fig. 1 comprises the U.S. Patent No. 7,540,881 of the people such as the Miller issued on June 2nd, 2009.Miller patent uses the traction drive of planetary ball bearing, the embodiment of continuous variable gearbox.The traction drive of Miller is limited to about 10,000rpm and makes Miller continuous variable gearbox cannot be used as high speed traction driving, and such as high speed traction drives 114.But Miller patent really discloses and a kind ofly uses traction drive and be suitable for use as the embodiment of the continuous variable gearbox that can be used as the continuous variable gearbox 116 shown in Fig. 1 to Fig. 3.The WilliamR.Kelley that on June 6th, 2006 is issued, Jr.'s and by the patent No.7 of transference BorgWarner, 055, another embodiment of the open continuous variable gearbox be applicable in 507.The U.S. Patent No. 5,033 of the Smith that on July 23rd, 1991 is issued, another embodiment of open continuous variable gearbox in 269.In addition, U.S. Patent No. 7,491,149 also disclose and a kind ofly will be suitable for use as the continuous variable gearbox of continuous variable gearbox 116.The Greenwood etc. announced on February 17th, 2009 be people's and openly can be used as the embodiment of the use traction-driven continuous variable gearbox of continuous variable gearbox 116 by the U.S. Patent No. 7,491,149 of transference Torotrak Co., Ltd.Be incorporated to especially by reference with the content of teaching disclosed in all these patents.August 9 nineteen ninety-five also explains with the European application No.92830258.7 announcing No.0517675B1 announcement another continuous variable gearbox 3 being suitable for use as continuous variable traction drive 116.

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

The embodiment of the high-speed driving of gear is openly used in the U.S. Patent No. 5,729,978 of the people such as the Hiereth of the U.S. Patent No. announcement on March 24th, 2,397,941 and 1998 of the Birgkigt that April 9 nineteen forty-six announces.Be incorporated herein especially by reference with the content of teaching disclosed in these patents.These references use master gear and do not use traction drive.Therefore, even if use is highly finished, specially designed gear train, the gear in these systems is limited to the rotational speed of about 100,000rpm or less.On November 1st, 2005 announce Kolstrup's and by transference RuloundsRoadtracksRotrexA/S U.S. Patent No. 6,960,147 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 the high-speed driving of the appropriate location of the high speed traction driving 114 that may be used for Fig. 1.U.S. Patent No. 6,960, is also incorporated herein by reference especially with the content of teaching disclosed in 147.

Fig. 2 is the schematic side elevational perspective view of super-turbocharger 100.As shown in Figure 2, turbine 102 has the exhaust manifolds 104 receiving and be applied to the exhaust of turbofan 130.Compressor 106 has the air-pressure duct 108 pressurized air being supplied to inlet manifold.The fenced compressor fan 126 of compressor shell 128 and be coupled to air-pressure duct 108.Disclosed in above, high speed traction drives 114 to be the fixed ratio traction drive being coupled to continuous variable gearbox 116.Continuous variable gearbox 116 live axle 118 and pulley 120.

Fig. 3 A is the side perspective of the embodiment of illustrated super-turbocharger 100 in Fig. 1 and Fig. 2.Moreover as shown in fig. 3, turbine 102 comprises turbofan 130, and compressor 106 comprises compressor fan 126.The axle (not shown) connecting turbofan 130 and compressor fan 126 is coupled to high speed traction and drives 114.Rotating mechanical energy drives 114 to be sent to driving gear 132 from high speed traction, and rotating mechanical energy is sent to CVT gear 134 and continuous variable gearbox (CVT) 116 by driving gear 132.Continuous variable gearbox 116 is coupled to axle 118 and pulley 120.

Fig. 3 B is the schematic cross sectional view of another embodiment of the super-turbocharger 300 being coupled to motor 304.As shown in Figure 3 B, turbine 302 and compressor 306 are mechanically coupled by axle 320.Rotating mechanical energy is sent to driving gear 322 or receives rotating mechanical energy from driving gear 322 by high speed traction driving 308.The specific embodiments that high speed traction drives 308 is illustrated in Fig. 3 B.Driving gear 322 transmits rotating mechanical energy between traction drive 308 and continuous variable gearbox 110.The specific embodiments of continuous variable gearbox 310 is also illustrated in 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 schematic sectional drawing of the modification of the embodiment of illustrated super-turbocharger 100 in Fig. 1, Fig. 2 and Fig. 3 A.As shown in FIG. 3 C, turbine 102 and compressor 106 are coupled by axle (not shown).High speed traction drives 114 to be coupled to described axle.Rotating mechanical energy drives 114 to be sent to driving gear 132 from high speed traction, and rotating mechanical energy is sent to gearbox gear 134 by driving gear 132.High speed traction driving 114, driving gear 132 and gearbox gear 134 can all be contained in same enclosure.Gearbox gear 134 is connected to gearbox 140, and gearbox 140 can comprise manual gearbox, CVT, d-axis, automatic gearbox 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 an alternate embodiment, pulley 120 is coupled to electric motor/generator 142.

Fig. 4 is the perspective schematic view using the high speed traction being coupled to continuous variable gearbox 408 to drive another embodiment of the super-turbocharger 400 of 416.As shown in Figure 4, turbine 404 compressor/turbine shaft 414 is mechanically coupled to compressor 402.Between compressor/turbine shaft 414 and multipath traction drive 416, rotating mechanical energy is transmitted in hereafter disclosed more in detail mode.Driving gear 418 transmits rotating mechanical energy between multipath traction drive 416 and the CVT gear 420 of continuous variable gearbox 408.Axle 410 and pulley 412 are coupled to continuous variable gearbox 408 and transmit power between continuous variable gearbox 408 and propelling are.

Fig. 5 is the side elevational cross-section schematic diagram of the multipath traction drive 416 being coupled to driving gear 418, and driving gear 418 is then coupled to CVT gear 420.As hereafter open in more detail, compressor/turbine shaft 414 has polished, hardening surface on central part, and the fixed star that described surface is used as in multipath traction drive 416 drives.

Fig. 6 is the exploded view 600 of the embodiment of illustrated super-turbocharger 400 in Fig. 4.As shown in Figure 6, the accommodating turbofan 604 of turbine case 602.Hot side cover plate 606 is arranged near turbofan 604 and main shell supporting element 608.Lip ring 610 seals the exhaust at hot side cover plate 606 place.Circular-cylindrical bearing 612 is arranged in circular-cylindrical 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 arranged on planet carrier 620.Multipath circular-cylindrical 622 is connected to planet carrier 620 rotatably.Fuel supply line 624 is used for supply of traction 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 arranged on planet carrier 626 outside.Cage 632 is arranged between retaining ring 630 and cold side cover plate 636.Compressor fan 638 is coupled to compressor/turbine shaft 414.The fenced compressor fan 638 of compressor shell 640.Main shell supporting element 608 also supports continuous variable gearbox and driving gear 418.Various bearing 646 is used for installing driving gear 418 and main shell supporting element 608.Continuous variable gearbox comprises CVT lid 642 and CVT bearing plate 644.It is inner that CVT gear 420 is arranged on main shell supporting element 608 with bearing 650.Relative with CVT bearing plate 644, CVT bearing plate 652 is arranged on the opposite side of CVT gear 420.CVT covers the various piece of 654 cover cap CVT devices.Axle 410 is coupled to continuous variable gearbox.Pulley 412 to be arranged on axle 410 and axle 410 and advance be between transmit rotating mechanical energy.

Fig. 7 is the primary clustering separated 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 is placed in the inclined surface for ball slope on retaining ring 630.As hereafter open in more detail, circular-cylindrical 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 hardened and forms with polishing the traction surface being used as sun roller 674, and sun roller 674 has the traction interface 676 connect with multipath planet rolling barrel 664 boundary.Multipath planet rolling barrel 664 rotates along multipath planet rolling barrel axle 672.Multipath planet rolling barrel 664 contacts retaining ring 630 at planet rolling barrel 664 with interface 690 place of retaining ring 630.Multipath planet rolling barrel 664 is at interface 691 place contact circular-cylindrical 614, and different from interface 691, there is different radial distances at interface 691 apart from multipath planet rolling barrel axle 672.Fig. 8 also illustrates planet carrier 626 and the ball slope 630 crossing with ball 656, and the ball slope 631 crossing with ball 660.Ball 656,658,660,662 is wedged between the ball slope (such as ball slope 630) on shell (not shown) and retaining ring 664.When moment of torsion is applied to circular-cylindrical 614, this causes retaining ring 664 slightly to move in the sense of rotation of circular-cylindrical 614.This causes ball to move up each ball slope, such as ball slope 630,631, and this then causes retaining ring 630 to be pressed against multipath planet rolling barrel 664,666,668.Because the interface 691 of planet rolling barrel 664 with retaining ring 630 tilts, and multipath planet rolling barrel 664 tilts with the interface of circular-cylindrical 690, so multipath planet rolling barrel 664 produces inside power, this generation power in traction interface 676 increases the traction at traction interface 676 place between multipath planet rolling barrel 664 and sun roller 674.In addition, produce power at multipath planet rolling barrel 664 and interface 691 place of circular-cylindrical 614, this increases the traction at interface 691 place.Equally as shown in Figure 8, compressor fan 630 and turbofan 604 are all coupled to compressor/turbine shaft 414.Equally as shown in Figure 8, circular-cylindrical 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 rotates in the clockwise direction, as shown in by sense of rotation 686.Multipath planet rolling barrel 664,666,668 has external diameter cylinder surface, the external diameter cylinder surface 688 of such as multipath planet rolling barrel 664.These external diameter cylinder surfaces contact sun roller 674, this causes multipath planet rolling barrel 664,666,668 to rotate in the counterclockwise direction, the sense of rotation 684 of such as multipath planet rolling barrel 666.Multipath planet rolling barrel 664,666,668 also has internal diameter cylinder surface, the internal diameter cylinder surface 680 of such as multipath planet rolling barrel 664.The cylinder surface 687 of the internal diameter cylinder surface contact circular-cylindrical 614 of each multipath planet rolling barrel.Therefore, planet rolling barrel 664 is formed in the interface 678 of the cylinder surface 687 of circular-cylindrical 614 traction interface transmitting rotating mechanical energy when applying draw fluid.The traction interface of rotating mechanical energy is transmitted at interface between each and sun roller 674 of multipath planet rolling barrel 664,666,668 after being also formed in the applying of draw fluid.

As above about pointed by Fig. 8 and Fig. 9, retaining ring 630 produces power, described in try hard to recommend dynamic multipath planet rolling barrel 664,666,668 towards sun roller 674 to produce traction.Each of multipath planet rolling barrel 664,666,668 is attached to planet carrier 626 rotatably with planet rolling barrel axle (the multipath planet rolling barrel axle 672 of such as multipath planet rolling barrel 664).These axles volume of traffic had slightly makes multipath planet rolling barrel 664,666,668 slightly to move and produce power between sun roller 674 and the external diameter cylinder surface (the external diameter cylinder surface 688 of such as multipath planet rolling barrel 664) of multipath planet rolling barrel 664,666,668.Multipath planet rolling barrel 664 also increases the traction of the interface of multipath planet rolling barrel 664,666,668 and circular-cylindrical 614 towards the movement of sun roller 674, and this is because the interface (such as interface 678) of multipath planet rolling barrel 664,666,668 and circular-cylindrical 614 tilts.The contact of the cylinder surface 687 of multipath planet rolling barrel 664,666,668 and circular-cylindrical 614 causes planet carrier 626 to rotate in the clockwise direction, all sense of rotation 682 as shown in Figure 9.Therefore, circular-cylindrical 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 that high speed traction drives another embodiment of 1000.As shown in Figure 10, axle 1002(its be the axle connecting turbine in super-turbocharger and compressor) sun roller in 1000 can be driven as high speed traction.Planet rolling barrel 1004 is at traction interface 1036 place engagement shaft 1002.Planet rolling barrel 1004 uses bearing 1008,1010,1012,1014 to rotate on axle 1006.Equally as shown in Figure 10, gear 1016 is arranged and is connected to the outer surface of carrier 1018.The bearing 1032,1034 that carrier 1018 is rotated by allowable carrier 1018 and gear 1016 is coupled to shell (not shown).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 moves, ball 1024,1026 moves respectively in ball slope 1028,1030, and forces retaining ring 1020,1022 inwardly each other.When ball 1024,1026 force fixed ramp 1020,1022 inwardly each other time, between the retaining ring 1020,1022 and the surface of planet rolling barrel 1004 at traction surface 1038,1040 place, produce power.As shown in Figure 10, the power produced by retaining ring 1020,1022 also forces planet rolling barrel 1004 downward, therefore between the axle 1002 and planet rolling barrel 1004 at traction surface 1036 place, produces power.Therefore, larger traction is realized in traction surface 1036 and traction surface 1038,1040 place.Draw fluid is applied to these surfaces, because draw fluid is heated, so draw fluid becomes viscosity and increases the friction at traction surface place owing to producing friction at traction surface 1036,1038,1040 place.

High speed traction driving 1000 shown in Figure 10 can with the High Rotation Speed more than 100,000rpm, and described speed cannot be reached by gear train.For example, high speed traction drives 1000 may rotate with the speed being greater than 300,000rpm.But high speed traction driving 1000 is limited to the gear ratio of about 10:1 because of the physical restriction of size.High speed traction drives 1000 can use three planet rolling barrels, such as around the planet rolling barrel 1006 of axle 1002 radial arrangement.As shown in Figure 9, the size of planet rolling barrel is limited relative to sun roller.If the diameter of the planet rolling barrel in Fig. 9 increases, so planet rolling barrel is by adjacent to each other.Therefore, as shown in Figure 10, only the gear ratio of about 10:1 can reach by planet traction drive, and as shown in Fig. 7 to Fig. 9, and the multipath planetary drive being connected to planet carrier can have the ratio up to 47:1 or larger.Therefore, if the more puffer that effectively must rotate with 300,000rpm needs compressor, so as shown in Fig. 7 to Fig. 9, the maximum rotation of 300,000rpm can be decelerated to about 6,400rpm by the traction drive of 47:1 ratio.Then, the continuous variable gearbox of master gear or traction can be used for driving at high speed traction transmitting rotating mechanical energy between the propelling system of motor.

Disclosed in above, the high speed traction shown in Figure 10 drives 1000 can have ratio large as 10:1.The rotational speed supposing the axle 1002 of the super-turbocharger of mini engine is 300,000rpm, and 300,000rpm rotational speeies of so described axle can be reduced to 30,000rpm at gear 1016 place.Can use the continuous variable gearbox 116 of various species, it uses master gear technical operation up to 30,000rpm.Traction-driven continuous variable gearbox (all traction-driven continuous variable gearboxes 116 as shown in fig. 11 and fig) also can be used as the continuous variable gearbox 116 shown in Fig. 1.In addition, the ratio up to 100:1 can realize by the multipath traction drive 416 shown in Fig. 4 to Fig. 9.Therefore, may need with 900, the mini engine of 5 liters of the compressor of 000rpm operation can be reduced to 9,000rpm, and this easily can be used in the rotational speed advancing system with the rotating mechanical energy that is coupled between turbine/compressor axle by various continuous variable gearbox 116.

Figure 11 and Figure 12 diagram can be used as the embodiment of the traction drive gearbox of the continuous variable of the continuous variable gearbox 116 of Fig. 1.Traction-driven continuous variable gearbox shown in Figure 11 and Figure 12 by present circle on the surface in a lateral direction translation seat ring 1116,1118 operate, described raceway surfaces has the radius of curvature of the contact position movement causing ball bearing, and described movement then causes ball to rotate with friction speed driving seat ring 1122 with different rotary angle.In other words, the contact position of each of the described bearing in raceway surfaces changes due to the transverse translation of seat ring 1116,1118, and this changes the rotational speed of described bearing at contact position place, as hereafter explained in more detail.

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 input gear 1104 of input shaft 1102 can drive 114 to be coupled to super-turbocharger by high speed traction, as shown in fig. 3.In this way, advance the input torque of system in order to drive the tooth bar input gear 1104 of input shaft 1102.The structure (comprising input seat ring 1114) that input torque on tooth bar input gear 1104 makes input shaft 1102 associate with it rotates in sense of rotation 1112.Input seat ring 1116 also responds to be authorized to the moment of torsion of input seat ring 1116 from input shaft 1102 by tooth bar 1166 and rotates around running shaft 1106.The rotation on multiple ball bearing 1132 is authorized in the rotation of input shaft 1102, input seat ring 1114 and input seat ring 1116, this is because permanent seat ring 1120 stops ball bearing in the rotation at the point of contact place with permanent seat ring 1120.Input seat ring 1114 and input seat ring 1116 rotate, this is because they are coupled by tooth bar 1116 with same angular velocity.Input seat ring 1114 and input seat ring 1116 cause ball bearing 1132 to determine to rotate up substantially vertical, and this is because ball bearing 1132 contacts permanent seat ring 1120.Ball bearing 1132 also causes ball bearing 1132 around the periphery precession of seat ring 1114,1116,1118,1120 against the contact of permanent seat ring 1120.In the embodiment depicted in fig. 11, the ball bearing 1132 reaching 20 rotated on the surface of seat ring 1114,1116,1118,1120 can be there is.Ball bearing 1132 is rotated in due to what driven by input seat ring 1114 and input seat ring 1116 and caused the tangential contact exporting and seat ring 1118 is set up ball bearing 1132.Depend on the contact position of the ball bearing 1132 exported on seat ring 1118, input seat ring 1114,1116 can change relative to the ratio of the rotational speed exporting seat ring 1118.Export seat ring 1118 and be coupled to output gear 1122.Output gear 1122 engages output gear 1124, and output gear 1124 is then connected to output shaft 1126.

The mode that traction-driven continuous variable gearbox 1100 shown in Figure 11 changes the ratio between input shaft 1102 with output shaft 126 realizes by changing the relative position of the point of contact between four seat rings 1114,1116,1118,1120 of contacting with ball bearing 1132.The mode that the contact surface of seat ring 1114,1116,1118,1120 and ball bearing 1132 changes is by changing the position that translation presss from both sides 1152.As shown in Figure 11, translation folder 1152 responds electric actuator 1162 and moves horizontally.Electric actuator 1162 has the telescopic speed changer 1158 of joint and makes the axle that telescopic speed changer 1158 rotates.Telescopic speed changer 1158 has different screw thread kinds on inside and outside.The difference of the pitch of different screw thread kind causes translation press from both sides the rotation of the axle of 1152 response electric actuators 1162 and move horizontally, and this authorizes the rotation in telescopic speed changer 1158.Press from both sides with bearing the transverse translation that 1164 translations contacted press from both sides 1152 and cause the transverse translation inputting seat ring 1116 and export seat ring 1118.In embodiment in fig. 11, the transverse translation of input seat ring 1116 and output seat ring 1118 can change about 1/10th inches.The contact angle that input seat ring 1116 and the translation exporting seat ring 1118 change ball bearing 1132 and export between seat ring 1118, this is because permanent seat ring 1120 and input seat ring 1114 and input the change of the contact angle between seat ring 1116 and change the mobile ratio of ball bearing 1132 in described seat ring or speed.The combination of the change of the angle between described seat ring allows that ball bearing 1132 and the exposure rate exported between seat ring 1118 or point of contact change, this cause 0% of the rotational speed of input shaft 1102 to as high as input shaft 1102 rotational speed 30% between velocity variations.In input shaft 1102 rotational speed 0% to 30% the velocity variations of output seat ring 1118 the large-scale adjustable rotating speed that can reach at output shaft 1126 place is provided.

In order to ensure the suitable clamping of ball bearing 1132 between seat ring 1114,1116,1118,1120, provide spring 1154,1156.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 against ball bearing 1132 remain in the whole translation distance of translation folder 1152.Telescopic speed changer 1158 has the screw thread being connected to retaining thread device 1160 on an internal surface.Retaining thread device 1160 is fixed to shell 1172 and provides the fixed position relative to shell 1172, and making translation press from both sides 1152 can the translation in the horizontal direction because of the different screw thread 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 all above rotates and the rotation 1128 of output gear 1122 at equidirectional (i.e. sense of rotation 1112).Clamping nut 1168 spring 1156 is retained on appropriate location and pre-loaded spring 1156 and permanent seat ring 1120 and input seat ring 1114 between produce suitable diagonal angle pressure.As shown in Figure 11, when 1152 horizontal translation is 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 is moved, and contacts the point of seat ring 1114 to 1120 and the described seat ring specific contact angle relative to ball bearing 1132 according to ball bearing 1132.Shell 1170 is bolted to shell 1172 tightly to hold 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 ball bearing 1132 has in four seat rings 1114,1116,1118,1120 advances 1131.As shown in Figure 11, the sense of rotation 1112 of axle 1102 causes the rotation of gear 1122 in 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 place.Seat ring 1116 contacts ball 1132 forcefully at contact position 1136 place.Seat ring 1118 contacts ball 1132 forcefully at contact position 1138 place.Seat ring 1120 contacts ball 1132 forcefully at contact position 1140 place.Each of contact position 1134,1136,1138,1140 is positioned in the common great circle on the surface of ball 1132.Described great circle is arranged in the plane holding the center of ball 1132 and the axle 1106 of axle 1102.Ball 1132 rotates around the running shaft 1142 at the center through ball 1132 and splits the described great circle holding contact position 1134,1136,1138,1140.Running shaft 1142 and the vertical shaft 1144 angled 1146 of ball 1132 tilt.The tilt angle 1146 of each be arranged in around the 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 is the ratio between the first distance 1148 and second distance 1150, and the first distance 1148 is the perpendicular distances from running shaft 1142 to contact position 1134, and second distance 1150 is the perpendicular distances from running shaft 1142 to contact position 1136.This distance rates equals described peripheral velocity ratio.Described peripheral velocity ratio is the ratio between the first peripheral velocity and the second peripheral velocity, wherein said first peripheral velocity is the difference between ball 1132 other ball in the peripheral velocity at seat ring 1114 place and the common rail peripheral velocity of ball 1132 and described seat ring, and described second peripheral velocity is the difference between the peripheral velocity of ball 1132 on seat ring 1116 and the common rail peripheral velocity of ball 1132, and be arranged in other ball in described seat ring.The radius of curvature that the radius of curvature of each of seat ring 1114 to 1120 is not necessarily constant, and can change.In addition, the radius of curvature of each of described four seat rings is not necessarily equal.

When seat ring 1116,1118 is in the upper translation simultaneously of horizontal direction (such as transverse translation direction 1108), the velocity rate of the rotation of axle 1102 and sense of rotation 1112 change relative to the rotation of gear 1122 and sense of rotation 1128, and the translation of seat ring 1116,1118 on horizontal direction 1108 causes the 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 relative to axle 1102.

As noted above, continuous variable gear box output end and the traction drive reducing gear Gear Contact being connected to turbocompressor axle.As noted above, at least two or three different types of traction drive deceleration system can be used.Typical kind is the planetary traction drive for high deceleration disclosed in Fig. 6 to Fig. 9 and Figure 10.If need large speed difference between turbine shaft and planet rolling barrel, so the embodiment of Figure 10 only can use two cylinders instead of three, so that the gear ratio needed for obtaining changes.

When three cylinders, there is the deceleration restriction of about 10:1, and the gearbox of about 20:1 may be needed obtain at a high speed 250,000rpm operations, lower than 10:1 gearbox required for 25,000rpm.Therefore, in Fig. 10, the appropriate location in three planetary drive systems can use two cylinder planet traction drive, to realize the most deceleration needed for High Speed System of smallest.Two cylinders also provide less inertia, because each cylinder is to thinking that described system increases a certain amount of inertia.In order to minimum inertia, two cylinders should be enough.The width of haulage drum is slightly wider than three cylinder embodiments.

The multipath planet rolling barrel rolled against axle is made up of elastic material, and such as spring steel or other materials, a little distortion of cylinder in outer cylinder allowed by described material.The application of spring-loaded cylinder can provide the required pressure on axle but restrictive axes can not find the ability of its desirable rotating center.

When turbosupercharger operates with hypervelocity, it has the Constraints of Equilibrium causing axle must find the rotating center of himself.Movement by central shaft compensates by described balance.This moves and can be compensated by spring-loaded cylinder.Described spring-loaded cylinder can also by being made for the thin steel band of not allowing that it operates against axle with very little inertia and being made for extremely light weight.Tape thickness is sufficiently thick and in traction surface, give enough pressure to provide the normal force needed for traction.Cam follower can be arranged in cylinder, and described cam follower is by each for location cylinder and described position is fixed in system.Cylinder must operate between outer cylinder and turbine/compressor axle with very straight linear array, but the key reducing inertia is lightweight.Can use one or two cam follower that steel band is retained on appropriate location, suitable described steel band is arranged in a linear and stops in the system.

Circular-cylindrical 614 is connected to gear on the outer surface and makes described circular-cylindrical power transmission can be entered or transfer out multipath traction drive 416.Circular-cylindrical 614 can be made in many ways.Circular-cylindrical 614 may simply be the solid members that torque transfer maybe can be entered or transfer out other suitable materials of multipath traction drive 416 by steel.Circular-cylindrical 614 can by allowing that circular-cylindrical 614 is that many materials of lightweight are made, but circular-cylindrical 614 must be made up of the material on the traction drive surface that can be used as on cylinder surface 687.Suitable cylinder surface 687 allows that planet rolling barrel 664,666,668 is by traction transfer of torque.

Turbine/compressor axle 414 also must keep in point-device linear array.Turbine/compressor axle 414 linear array is in the enclosure allowed and is maintained gap between the top of the blade of compressor and compressor shell.Tighter gap increases compressor efficiency.More accurate position reduces the touch opportunity between turbocompressor fan 638 and compressor shell 640.A kind of control is needed to guarantee to there is minimum clearance by the method for the thrust load caused against compressor wheel pressurized gas.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 has come.

In turbosupercharger, be the object of reliability, bearing normally all has the Casing bearing of oil-gap in inner side and outer side, to allow turbine shaft when its harmonious rotation by himself centering.The requirement of balance of the turbosupercharger of high volume manufacture is by using double gap bearing to reduce.Because need the more accurate linear array of the axle of tighter gap and turbosupercharger, these kinds of bearings are used.Ball bearing is used for fixing compressor and turbine and better align with shell seen by lateral movement perspective view for keeping.This can have been come by one or two ball bearing.The linear array of the bearing in the perimeter of being pressurizeed by oil is allowed described bearing floating and is allowed that described bearing finds center.This affects shell, gap between turbine and compressor outward edge really, but allows and keep little thrust clearance.Turbine shaft bearing provides the 3rd restriction point to keep the linear array of cylinder.Cam follower in the middle of described cylinder can make described cylinder mutually keep 120 degree.Each cylinder can use two little cam followers to eliminate the backlash caused when power changes direction.

Also larger turbine can be used.The diameter of turbine wheel can be made for and be greater than normal dia.Turbine external diameter even can be made to be greater than compressor wheel, and can not to reach the top close to the critical velocity of velocity of sound part, this is because exhaust gas density is lower than intake air and therefore velocity of sound is higher.This allows that exhaust produces more moments of torsion and without higher back pressure on turbine/compressor axle.Having high torque causes described turbine to regain energy more more than the energy be compressed into needed for mouthful air.This produces than can regaining and transferring to the more energy of the energy of motor.The unwanted more multipotency measuring cup from identical exhaust stream of compression institute is sent to arbor and the lower fuel consumption of generation.

In addition, the guide vane controlling to be vented the entry angle banging into turbine wheel can be used to improve turbine efficiency.This makes peak efficiencies higher, but shortens the velocity range that implementation efficiency depends on.Narrow velocity range is unfavorable for conventional turbochargers, and is not problem for the super-turbocharger that manager can provide required speeds control.

Compared with the pressure striding across compressor, the higher back pressure striding across turbine can also produce unbalanced super-turbocharger.For conventional turbochargers, this pressure difference is contrary.Having higher back pressure causes described turbine to regain energy more more than the energy be compressed into needed for mouthful air.This produces than can regaining and transferring to the more energy of the energy of 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, this is because conventional turbochargers cannot be uneven and do not exceed the speed limit.Increase back pressure and be unfavorable for petrol engine and natural gas engine, this is because it increases the air displacement of catching in cylinder, this makes motor more may have explosion issues.

According to another embodiment, the second turbine wheel can be positioned at the energy that turbine/compressor axle increases and is regained by described turbine and improve the fuel efficiency of engine system.Equally, the second compressor wheel can be positioned at the boost potential that same axis increases super-turbocharger and allow the cooling during rolling between level.This makes inlet temperature colder and therefore reduces NOx for given boosting.

In addition, the through flap apex of turbine blade cooling can be provided to reduce the temperature in high temperature application.This can have been come by the outer peripheral hollow airfoil top of described turbine.This special tip designs adds turbine efficiency and is provided for the path of cooling-air through described blade.Turbine airfoil cooling can also be supplied to the pressurized air of dorsal part that turbine takes turns and provides by striding across from compressor side shell.In addition, heat pipe can be used to cool described turbine wheel and blade.

In addition, power path can use moment of torsion softening installation.Can to make to remove before entering shell from motor or the mode that advances the moment of torsion of system to promote and do not lose described energy to the rotating mechanical energy making arbor energy or come self-propelled system through curved axis or promote softening installation (spring loads or flexure).By affecting gearbox without the torque peak in traction drive, reduce Peak torque demand.By eliminating these torque peaks, traction drive is more reliable, this is because traction requirements is limited to the Maximum Torque in system.By minimizing these torque peaks in traction drive, described traction-driven size and contact surface area can be minimized.Minimum contact surface area maximizes the efficiency of described system, and still can realize transmitting the moment of torsion needed for continuous power.

Or and according to another embodiment, axle, line belt can be used in or eat the variable speed traction drive design that the appropriate location driven has fixed displacement hydraulic pump.This makes described system be easier to encapsulation, and this is particularly useful for the very large motor with multiple turbosupercharger.

In fig. 13 in another embodiment illustrated, the second super-turbocharger uses a gearbox as the mode obtaining elevated pressures ratio, and as being obtained the mode of colder inlet temperature by use second interstage cooler.This may because of the fixed speed ratio between two super-turbocharger.First super-turbocharger 1302 has air inlet duct 1308 and compresses the air being supplied to motor from air-pressure duct 1310.Exhaust manifolds 1314 exhaust received from described motor runs the turbine of the first super-turbocharger 1302.Exhaust outlet conduit 1312 is discharged in exhaust.First super-turbocharger 1302 driving gear 1306 is coupled to the second super-turbocharger 1304.

Figure 14 A illustrates the schematic diagram of another embodiment carried into execution a plan of use two super-turbocharger (such as low pressure super-turbocharger 1402 and high-voltage super turbosupercharger 1404).The super-turbocharger of standard is bad to regain when outlet valve first time opens the high-voltage pulse produced by cylinder.As shown in fig. 14 a, regain to improve this promotion pressure, the high pressure gas valve port 1406,1408 of the motor of four valves is separated with low pressure exhaust valve port 1410,1412.High-pressure exhaust 1406,1408 is directed to high-pressure turbine 1434 by high pressure gas manifold 1430, and low pressure exhaust mouth is directed to low-pressure turbine 1420 by low pressure exhaust manifold 1428.By changing the valve sequential in high-pressure exhaust 1406,1408, first the valve on high-pressure exhaust 1406,1408 is opened and opening towards high-pressure turbine 1434, regain pulse energy better.Valve quick closedown on high-pressure exhaust 1406,1408, and the valve then on low pressure exhaust mouth 1410,1412 is opened within whole period of exhaust stroke.Valve opening on low pressure exhaust mouth 1410,1412 is towards low-pressure turbine 1420.This process reduces the work needed for piston when cylinder is vented.The standby fuel efficiency of this process improvement, or supplementary loss when at least eliminating standby.The outlet of high-pressure turbine 1434 is also connected to low-pressure turbine 1420.Catalytic type diesel particulate filter (not shown) also can be arranged in comparatively before low-pressure turbine.

Equally as shown in fig. 14 a, EGR conduit 1438 is connected to high pressure gas manifold 1430.EGR conduit 1438 is allowed that the part from the exhaust of high pressure gas manifold 1430 is guided by cooler 1440 and EGR valve 1442 and is back to inlet manifold 1444.The exhaust from high pressure gas manifold 1430 of being guided by EGR conduit 1438 is led to the object of inlet manifold 1444 for exhaust gas recirculatioon.The exhaust flowing through exhaust gas recirculatioon conduit 1438 assists to reduce the combustion temperature in combustion chamber, after especially cooling in cooler 1440.Described exhaust is containing wetly and other liquid, and therefore the temperature that its assistance reduces combustion chamber reduces the NOx emission from motor.The amount of exhaust gas recirculation is controlled by EGR valve 1442.EGR valve 1442 can (such as by use throttle valve) be fixing maybe can depend on the NOx emission of being monitored of motor and change.

Equally as shown in fig. 14 a, high-pressure air is leaked to inlet manifold 1444 from high pressure compressor 1432 by high pressure compressor manifold 1446.Therefore, inlet manifold 1444 keeps the predetermined high-pressure level indicated by the output terminal of high pressure compressor 1432.In order to make recycle gas flow through EGR conduit 1438, the pressure in high-pressure manifold 1430 must higher than the pressure in inlet manifold 1444, indicated by the delivery pressure by high pressure compressor 1432.So, valve in high-pressure exhaust 1406,1408 is sufficiently early opened during the downward stroke of piston, and at this moment residual pressure is still present in piston to produce enough pressure to drive the exhaust of passing EGR conduit 1438 from high pressure gas manifold 1430 in high pressure gas manifold 1430.Disclosed in hereafter, the point that the valve in high-pressure exhaust 1406,1408 exists a small amount of energy loss in the process of downward driven plunger is opened.Opening a little early than bottom dead center of high pressure valve, but the maximum torque point exceeding arbor upper piston, this upper boom is roughly in 90 °.This point occurs in about 100 °.The cosine of an angle value of torque capacity and bar is proportional, and make the piston when high pressure valve is opened lower, the energy lost during driven plunger is fewer.But the residual pressure of residual q.s in cylindrical chamber, this can be discharged from cylindrical chamber by high pressure valve before arrival bottom dead center, and it can make it enter high-pressure turbine 1434 in order to drive the exhaust in EGR conduit 1438.By use high-pressure exhaust 1406,1408 high pressure valve preexhaust described in cylinder, a large amount of residual pressures in cylinder were discharged before opening low pressure exhaust mouth 1410,1412.When open, low pressure exhaust mouth 1410,1412 can discharge most of pressure from cylinder.So, the residual pressure in cylinder reduces NOx emission through EGR conduit 1438 in order to guiding exhaust and drives high-pressure turbine 1434, and this adds extra power and efficiency for motor.

Equally as shown in fig. 14 a, from the exhaust of low pressure exhaust manifold in order to drive the low-pressure turbine 1420 of low pressure super-turbocharger 1402.The exhaust of being discharged by high-pressure turbine 1434 is combined with the low pressure exhaust from low pressure exhaust mouth 1410,1412 and drives low-pressure turbine 1420.Exhaust from low-pressure turbine 1420 is discharged by relief opening 1436.Low-pressure turbine 1420 is coupled to low pressure compressor 1418, and low pressure compressor 1418 compresses the intake air 1422 of prearranging quatity.Pressurized air is directed to the input end of high pressure compressor 1432 by conduit 1424 from low pressure compressor 1418, high pressure compressor 1432 forced air be used in compression 1424 further produces the pressurized air of more high pressure, and the pressurized air of described more high pressure is directed to inlet manifold 1444 by high pressure compressor manifold 1446.

Figure 14 B illustrates the change scheme of the embodiment shown in 14A.As shown in Figure 14 B, high-pressure exhaust 1406,1408 is bonded to and is coupled in the high pressure gas manifold of high-pressure turbine 1434.In other words, the whole high pressure gas from high pressure gas manifold 1430 are applied to high-pressure turbine 1434 to drive high-pressure turbine 1434, and this then drives high pressure compressor 1432.High pressure compressor 1432 receives the pressurized air conduit 1424 from the low pressure compressor 1418 of the compression intake air 1422 of low pressure super-turbocharger 1402.The output of high pressure compressor 1432 is supplied to input manifold 1444 by 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 low pressure exhaust manifold 1428, and described low pressure exhaust discharged by low pressure exhaust mouth 1410,1412.Exhaust from low-pressure turbine 1420 is discharged by relief opening 1436.Drive the pressurized gas from high pressure gas manifold 1430 of high-pressure turbine 1434 to be coupled to exhaust gas recirculatioon (EGR) conduit 1426 and transmit and be back to inlet manifold 1444.Drive the pressure of the pressurized gas from high pressure gas manifold 1430 of high-pressure turbine 1434 can not reduce substantially and there is sufficiently high pressure and the exhaust from EGR conduit 1426 is pressed in inlet manifold 1444.Figure 14 B provides the maximum minimizing of NOx gas, and this is because the whole in essence exhausts from high pressure gas manifold 1430 are all recycled to inlet manifold 1444.

Equally as shown in Figure 14 B, waste gas valve 1448 can be used by high pressure gas from high pressure gas manifold 1430 bypass to EGR conduit 1426.Sometimes high pressure gas may be too warm and/or may provide the exhaust being in and can excessively driving under the pressure of high-pressure turbine 1434.In this case, waste gas valve 1448 can be opened and a part for high pressure gas is directly supplied to EGR conduit 1426 from high pressure gas manifold 1430.In addition, can increase EGR valve 1450, EGR conduit 1426 is connected to low pressure exhaust manifold 1428 by it.If enough air displacemenies are supplied by EGR conduit 1426, so a part for those gases can be directed to low pressure exhaust manifold 1428 by EGR valve 1450 from EGR conduit 1426.Then, running low-pressure turbine 1420 can be used for from the too much gas of EGR conduit 1426 to come by increasing entrance mainfold presure 1444 and increase extra power to motor.The use of EGR valve 1450 provides and can regain recycle gas and increase extra power to motor and improve the additional ways of the operating efficiency of motor.

Another modification of the embodiment of Figure 14 C pictorial image 14A and Figure 14 B.As shown in Figure 14 C, intake air 1422 is compressed by low pressure compressor 1418.Pressurized air from low pressure compressor 1418 supplies inlet manifold 1444 by conduit 1424.Same as shown in Figure 14 C, do not use the second high-pressure turbine and whole recycle gas is recycled to inlet manifold 1444 from high-pressure exhaust 1406,1408 by EGR conduit 1426.Exhaust from low pressure exhaust mouth 1410,1412 is bonded in conduit 1428 and operates low-pressure turbine 1420.Then, described exhaust is discharged at relief opening 1436 place.Therefore, be supplied to from whole gases to blowing down of high-pressure exhaust 1406,1408 and be back to inlet manifold 1444 to produce the larger minimizing of NOx gas.Or EGR valve 1450 can be used for a part for the exhaust in EGR conduit 1426 to be directed to low pressure exhaust manifold 1428, this adds other power and decreases the recirculating gas scale of construction in EGR conduit 1426 to low-pressure turbine 1420.EGR valve 1450 can be adjusted to adjust the air displacement being supplied to low pressure exhaust manifold 1428 from EGR conduit 1426.If the NOx that enough air displacement recirculation in EGR conduit 1426 reduces motor exports, so this process can be useful.

Figure 14 D be top dead after valve stroke, cylinder pressure and flow velocity and the plotted curve of piston position.As shown in fig. 14d, 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.The lift of high pressure valve 1456 occurs about 100 ° and rotates and produce from high-pressure exhaust 1406,1408(Figure 14 A, Figure 14 B and Figure 14 C) the comparatively large surge downwards of high-pressure spray 1452 of discharging.Curve 1454 illustrates the lift of low pressure valve.Low pressure valve lift produces lowpressure stream 1458 in low pressure exhaust mouth 1410,1412.Therefore, the cylinder pressure 1450 in cylinder reduces further.

Figure 14 E is the PV plotted curve of piston cylinder pressure and cylinder volume when moving down in the cylinder and then move up.Nearly null representation top dead, and 1 represents the bottom dead center that cylinder rotates.Two curves shown in Figure 14 E.Curve 1464 represents the cylinder pressure of motor and the curve of volume that do not use and rely profit circulation.Curve 1462 is that diagram relies the cylinder pressure of sharp circulation means and the curve of cylinder volume, such as shown in Figure 14 A to Figure 14 C.As shown in Figure 14 A to Figure 14 C, at point 1466 place, high pressure valve is opened on bad sharp circulation means, and pressure reduces.Region 1468 between point 1466,1470 represents the energy lost by opening described high pressure valve.But, pointed by Figure 14 E, at point 1472 place, rely the pressure drop in sharp circulation means lower than the pressure in Fei Laili circulation means and in the whole process to point 1474, keep below the pressure of described Fei Laili circulation means.Between 1472 and point 1474, in cylinder, there is less pressure, this cause when cylinder to move to from point 1472 a little 1474 time cylinder less back pressure.Indicated the energy saved by the movement of piston in cylinder at low pressures by a large amount of regions between the 1478 bad sharp cyclic curves 1462 indicated and ordinary curve 1464 between point 1472 and 1476.

In an alternate embodiment, super-turbocharger can be used as the extraction pump for reprocessing, and for motor and eliminate only for the need of the separate pump of combustion furnace.

In another embodiment, provide manager's (not shown) to prevent excessive acceleration, keep compressor avoid surge condition and control the maximal efficiency of turbine and compressor.Super-turbocharger is unique compared with conventional turbochargers, this is because the peak value of turbine efficiency and the peak value of compressor efficiency can be at the same speed.Control this peak efficiencies speed in order to given boosting demand can be molded and be programmed in e-management person.Actuator can provide management, but electric shift case does not need actuator.

In another embodiment, the fuel loading system for super-turbocharger pulls the vacuum in shell, and therefore reduces the aerodynamic losses of high-speed assembly.

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

In another embodiment, the traction drive being used for gearbox and the deceleration from turbine shaft is used.Use ball bearing, draw fluid is also as oiling agent.During super supercharging, system improve load-receipt, reduce soot emissions, provide low side moment of torsion up to 30% increase and peak power up to 10% increase.During worm-gear combination, system provide improvement up to 10% gas saving and control back pressure.In order to motor downsizing, system provide allow motor little 30% to 50% 30% more low side moments of torsion, there is the motor vehicle fuel saving rate of the improvement of lower engine quality and 17% or more.Figure 15 diagram is used for the simulation BSFC improvement project of natural gas engine.

Catalyzer, DPF or even combustion furnace add turbine front that DPF also can be positioned at super-turbocharger by heating exhaust gas to the temperature higher than the temperature of motor.Higher temperature makes air expand, and makes the flow rate striding across turbine higher even further.About 22% of this heat increase can change the mechanical work striding across super-turbocharger into, presents the turbine efficiency of 80%.The relatively large exhaust being supplied to turbine can be slowed down turbine response and even produce larger turbo lag, but the traction drive 114 of super-turbocharger driving pressure response and continuous variable gearbox 116 overcome this problem.The people such as the VanDyne of application on July 24th, 2009 are entitled as the similar techniques openly using catalyzing type purifier in the international patent application No.PCT/US2009/051742 of " using super-turbocharger to improve piston-engined fuel efficiency " (" ImprovingFuelEfficiencyforaPistonEngineUsingaSuper-Turbo charger "), are incorporated herein especially by reference disclosed in described application with the content of teaching.

Figure 16 is the illustrated simplification single line drawing of an embodiment forming high efficiency, super turbo charged engine system 1600.As those skilled in the art will from the following describing solution, this super turbo charged engine system 1600 is specially adapted to the petrol engine of some spark ignitions used in diesel engine and passenger vehicle and commercial car, and the exemplary embodiment therefore discussed herein uses this environment to contribute to understanding of the present invention.But should recognize that the embodiment of system 1600 is applicable to other operating environments, for example, such as continental rise generator and other continental rise motor, adopt these embodiments should in order to illustrate instead of in order to limit.

As shown in Figure 16, super-turbocharger 1604 comprises turbine 1606, compressor 1608 and gearbox 1610, and gearbox 1610 is coupled to the arbor 1612 of motor 1602 or advances the other parts of system.Although do not need in all embodiments, the embodiment shown in Figure 16 also comprises interstage cooler 1614 and improves the density being supplied to the air of motor 1602 from compressor 108 and improve further from the available power of motor 1602.

Super-turbocharger has some advantage of turbosupercharger.Turbosupercharger uses the turbine by the exhaust gas drive of motor.This turbine is coupled to compressor, and described compressor compresses is supplied to the intake air in the cylinder of motor.Turbine in turbosupercharger is by the exhaust gas drive from motor.So, when first time accelerate until exist enough thermal exhausts carry out rotary turbine and be the compressor being mechanically coupled to turbine be provided with power to produce enough boosting time, it is sluggish that motor stands boosting.In order to minimize sluggishness, usually use less and/or lighter turbosupercharger.The less inertia of the turbosupercharger of lightweight allows that it quickly rotates, thus minimizes the sluggishness in performance.

Unfortunately, this turbosupercharger that is less and/or lightweight may exceed the speed limit when producing a large amount of exhaust stream 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 being arranged on turbine upstream.Described waste gas valve is the pressure actuated valves shifting some exhausts around turbine when the delivery pressure of compressor exceedes predetermined limit value.This limiting value is set in the pressure that the described turbosupercharger of instruction will exceed the speed limit.Unfortunately, this causes wasting the part from the available energy of the exhaust of motor.

Should recognize that traditional turbosupercharger sacrifices low end performance for high-end power, develop the device being known as super-turbocharger.The U.S. Patent No. 7 being entitled as " super-turbocharger " (" Super-Turbocharger ") that on February 17th, 2009 is issued, 490, describe this super-turbocharger in 594, be incorporated herein especially by reference with the content of teaching disclosed in this patent.

As in above-cited application discuss, in super-turbocharger, during low motor speed operation when engine exhaust hot not cannot be used for drive turbine time, compressor is driven by gearbox by the engine crankshaft being coupled to motor.The mechanical energy being supplied to described compressor by described motor reduces the turbo lag problem that suffers of conventional turbocharger, and allows the use more greatly or more turbine of efficiency and compressor.

Super-turbocharger 1604 shown in Figure 16 operates and does not suffer the turbo lag problem of conventional turbocharger low side to supply pressurized air from compressor 1608 to motor 1602 and be not wasted in the high-end available energy of engine exhaust heat from being supplied to turbine 1606.These advantages provide because comprising super-turbocharger gearbox 1610, during the various operator schemes of motor 1602, super-turbocharger gearbox 1610 can extract power from engine crankshaft 1612 and supplying power to engine crankshaft 1612 drives compressor 1608 respectively and loads turbine 1606.

Between the starting period, when conventional turbocharger due to lack drive turbine from the enough power of motor and suffer sluggishness time, super-turbocharger 1604 provides super supercharging behavior, obtains power thus drive compressor 1608 and provide enough boostings for motor 1602 by super-turbocharger gearbox 1610 from arbor 1612.When described motor reaches speed and is enough to drive turbine 1606 from the available amount of power of engine exhaust heat, the amount of power obtained from arbor 1612 by gearbox 1610 is reduced.After this, turbine 1606 continue supplying power to compressor 1608 make its compress intake air and give motor 1602 used.

When the engine speed increases, the point that the turbine 1606 from the available amount of power of engine exhaust heat is increased to wherein conventional turbocharger can exceed the speed limit.But, use super-turbocharger 1604, the too much energy being provided to turbine 1606 by engine exhaust heat is led to engine crankshaft 1612 by gearbox 1610, makes compressor 1608 remain on suitable speed for motor 1602 simultaneously and supplies desirable boosting.Larger from the available outputting power of the exhaust gas heat of motor 1602, the power produced by turbine 1606 being led to arbor 1612 by gearbox 1610 is more, keeps from the available the best boosting of compressor 1608 simultaneously.Turbine 1606 is prevented turbine 1606 from exceeding the speed limit by this loading of gearbox 1610 and is maximized the efficiency of the power extracted from engine exhaust.So, traditional waste gas gate is not needed.

Although can be severely limited to from the available amount of power of engine exhaust in order to drive the amount of power of turbine 1606 in the turbo charged application of conventional Super, if but the heat energy that can use completely and/or can have additional supply of to turbine blade and mass flow, so turbine 1606 can produce obviously more power.But turbine 1606 cannot operate and without damage on specified temp, and mass flow is limited to traditionally from motor 1602 exhaust out.

Recognize this point, the embodiment of system 1600 is by protecting turbine 1606 to avoid high temperature transition at turbine 1606 placed upstream catalytic type diesel particulate filter 1616.In one embodiment, catalytic type diesel particulate filter is placed on turbine upstream close to gas exhaust manifold, and this realizes the exothermic reaction causing the increase of delivery temperature during the lasting high speed or load operation of motor.Using catalytic type digital particle filter, energy can being regained from coal smoke, hydrocarbon and the carbon monoxide burnt at catalytic type diesel particulate filter 1616 for being positioned at the super-turbocharger increase power in catalytic type digital particle filter 1616 downstream.Can from have almost 100% soot collection rate very limited flow capacity conventional diesel particulate filter or by using circulation catalytic type digital particle filter to regain energy.Circulation catalytic type digital particle filter a kind ofly only collects only about half of coal smoke and the diesel particulate filter making second half pass.Two kinds of digital particle filters are all that catalytic type is so that burning has effulent at the temperature that appropriateness is low.The catalysis of digital particle filter is that coal smoke, hydrocarbon and carbon monoxide burn at low temperatures and realize by providing platinum coating to guarantee for particle filter element.In addition, diesel particulate filter and burner can be used to burnout to the coal smoke of the digital particle filter making super-turbocharger upstream.Petrol engine does not have enough coal smokes usually to needs diesel particulate filter.But the direct injection engine of some gasoline produces enough coal smokes and other particle, therefore use particulate filter possibility useful, and can launch to use catalytic type diesel particulate filter by mode disclosed herein.

In order to coolant exhaust before arrival turbine, the compressed-air actuated part produced by compressor is fed directly in the exhaust of turbine upstream by control valve 1618, and is added into the engine exhaust leaving catalytic type diesel particulate filter 1616.As described in greater detail below, colder intake air expands and cools described exhaust and be exhaust stream increase additional mass, and this adds extra power for turbine 1606.When colder air be provided to thermal exhaust remain in optimum temperature to the temperature of the mix flow making arrival turbine 1606 time, the energy and the mass flow that are delivered to described turbine blade also increase.This dramatically increases the power being provided with driving engine crankshaft by described turbine.

In order to not disturb the chemical reaction in super-turbocharger 1616, compressor feedback air is added into catalytic type diesel particulate filter 1616 downstream.In this embodiment, engine exhaust raises because of exothermic reaction through the temperature of catalytic type diesel particulate filter 1616 and described exhaust.Then, described compressor feedback air is added and the total mass flow increase making to be supplied to described turbine of expanding.Embodiment of the present invention control be supplied with coolant exhaust and drive the compressed feedback air quantity of described turbine to guarantee to be transported to described turbine compared with the combination of cold compression feedback air and engine exhaust for the optimum temperature that turbine blade operates.

Because the catalytic type diesel particulate filter 1616 shown in Figure 16 has the thermal mass larger than the exhaust from motor 1602, so originally catalytic type diesel particulate filter 1616 is operating as thermal center air valve, it prevents high temperature thermal spike from arriving turbine 1606.But, due to the reacting quintessence in catalytic type diesel particulate filter 1616 being heat release, so the delivery temperature leaving catalytic type diesel particulate filter 1616 is higher than the delivery temperature entering catalytic type diesel particulate filter 1616.As long as the delivery temperature entering turbine keeps below the maximum operating temp of turbine 1606, just do not have problems.

But in lasting high speed and the high capacity operation period of motor 1602, the discharge temperature that the transformation from catalytic type diesel particulate filter 1616 is vented can exceed the maximum operating temp of turbine 1606.As described above, the delivery temperature of discharging catalytic type diesel particulate filter 1616 reduces because supplying the compressed-air actuated part from compressor 1608 by feedback valve 1618, and mixes with the exhaust of discharging catalytic type diesel particulate filter 1616.Significantly improved gas saving by not using fuel to realize as freezing mixture in such cases, as in conventional systems do.In addition, the operation of gearbox is controlled allows that compressor 1608 is supplied enough air supplies and provides best boosting for motor 1602 and provide compressed feedback air to turbine 1606 by feedback valve 1618.Because the too much power produced by turbine 1606 caused by the mass flow by the compressed-air actuated increase of described turbine is led to arbor 1612 by gearbox 1610, still improve fuel efficiency further.

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 from the gas extraction power of about 950 ° of C by optimum operation, but can not higher and non-warping or possible breakdown.Because the material restriction of turbine blade, is issued to best power source at about 950 ° of C.Because delivery temperature is limited to about 950 ° of C by material, so supply more air to increase the performance that the mass flow striding across turbine improves described turbine under temperature extremes (such as 950 ° of C).

Although contribute to reducing from catalytic type diesel particulate filter 1616 delivery temperature out at the compressed feedback air stream of 200 ° of C to 300 ° of C, should recognize that can be used for when temperature and mass flow are maximized and are in the thermoae limit value of turbine 1606 should from the maximum power of turbine 1606.So, in one embodiment, feedback air amount is controlled make to be vented remain on the maximum allowable operating temperature (M.A.O.T.) of turbine with the combination of feedback air under or close to described maximum allowable operating temperature (M.A.O.T.), therefore maximize or significantly improve the amount of power being delivered to turbine.Due to compressor 1608, usually not need all these too much power be 1602 supplies the best boostings and supply compressor feedback air by feedback valve 1616, so described too much power can be transferred into the arbor 1612 of motor 1602 by gearbox 1610, therefore improve 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 turbine 1606 by the connection of feedback valve 1618.So, the air supply from described compressor is provided at the downstream of catalytic type diesel particulate filter 1616 not interrupt the chemical reaction in catalytic type diesel particulate filter 1616.Namely, in the embodiment using catalytic type diesel particulate filter 1616, too much oxygen can be caused to be provided to catalytic type diesel particulate filter 1616 in catalytic type diesel particulate filter 1616 supplied upstream compressor feedback air, prevent catalytic type diesel particulate filter 1616 from producing chemical reaction needed for proper handling thus.

The optimum efficiency of the power produced by turbine 1606 is reached during maximum temperature (in the material limits value of turbine self) due to the gaseous mixture when the exhaust in compressor feedback air and turbine blade, so the compressor feedback air amount entered by feedback valve 1618 is restricted, not reduce temperature making it significantly lower than this optimum temperature.Because catalytic type diesel particulate filter 1616 produces more heat energy by exothermic reaction and is increased to the temperature of more than the maximum operating temp of turbine 1606 from the temperature that the transformation of catalytic type diesel particulate filter 1616 is vented, so supply more compressor feedback air by feedback valve 1618, described compressor feedback air increases mass flow and is supplied to the energy of turbine 1606.Because the amount of the heat energy produced by catalytic type diesel particulate filter 1616 reduces, so the amount of the compressor feedback air of being supplied by feedback valve 1618 also can reduce, to avoid supply than required more air, this causes the temperature keeping gaseous mixture under optimal operating conditions.

In another embodiment, system uses feedback valve 1618 for being back in the exhaust of the turbine front portion under low speed high capacity serviceability, to avoid the surge of compressor compared with the supply of cold compression device air.To rotate with slow rpm due to motor and do not need too many intake air stream, so when compressor pressure uprises but the mass flow of allowing in motor is low, the surge of generation compressor.The compressor surge (aerodynamic force stall) caused by the low air flow striding across compressor blade causes the efficiency of compressor very rapidly to decline.When conventional turbochargers, enough surges can make turbine stop the rotation.When super-turbocharger, the power from engine crankshaft can be used to make its surge to promote compressor.Open feedback valve 1618 and allow that compressed-air actuated part feedback is at engine environment.This feedback flow makes compressor avoid surge and allows that higher boosting arrives motor 1602, allows that motor 1602 produces the ratio more power of issuable power under low engine speed usually thus.The total mass flow by compressor is preserved in the exhaust of pressurized air being injected turbine front portion, therefore all flows to and reaches turbine, this minimize the super power be pressurized to needed for high boost level of motor.

In another embodiment, extra cold start controlling valve 1620 can be comprised for the operation during rich engine cold-start.During this engine cold-start, the exhaust from motor 1602 generally includes too much unburned fuel.Due to this rich mixture and non-stoichiometry, so catalytic type diesel particulate filter 1616 fully can not reduce the unburned hydrocarbons (UHC) in exhaust.During this period, cold start controlling valve 1620 can be opened to provide compressor feedback air to supply required extra oxygen to the input end of catalytic type diesel particulate filter 1616 and drops to stoichiometric levels to make rich mixture.This allows that the weight of catalytic type diesel particulate filter 1616 alleviates quickly and more effectively reduces the discharge between cold start-up active stage.If motor is standby, so conventional turbochargers does not have boosting can supply feedback air.But the speed change ratio of gearbox 1610 can be adjusted to give the enough speed of compressor and flow through pressure needed for valve 1620 to produce air.So, the ratio that control signal 1624 can be used for adjusting gearbox 1610 makes in standby period, especially can by engine-driving axle 1612 for compressor 1608 provides enough rotational speeies make it flow through cold start-up valve 1620 to compress enough air and light catalytic type diesel particulate filter 1616 with enough amount of oxygen during cold start-up.

In cold start-up activity, the demand of extra oxygen is usually limited, and usually only continues 30 seconds to 40 seconds.Many vehicles generally include be separated extraction pump and between cold start-up active stage supply oxygen, compared with the restricted time amount needed for operating with this extraction pump, need great amount of cost and weight.By replacing being separated extraction pump with simple cold start controlling valve 1620, achieve a large amount of cost savings, weight savings and complexity saving.Because super-turbocharger 1604 can control the speed of compressor 1608 by gearbox 1610, so cold start controlling valve 1620 can comprise simple close/open valve.Then, the speed that can control compressor 1608 by gearbox 1610 under the operation of control signal 1624 controls the air quantity of supplying between cold start-up active stage.

If fuel is used as regardless of the negative effect to fuel efficiency in motor and/or for the freezing mixture of catalytic type diesel particulate filter 1616, so cold start controlling valve 1620 can also use in excessive temperature operation period.In this case, cold start controlling valve 1620 can be supplied required extra oxygen and makes rich exhaust decline be back to stoichiometric levels and allow that catalytic type diesel particulate filter 1616 suitably reduces unburned hydrocarbons in exhaust and discharges.This provides big advantages for the environment on previous system.

Wherein during cold start controlling valve 1620 close/open valve embodiment in, system can modulate cold start controlling valve 1620 to change the air supply of supply, to make exhaust drop to stoichiometric levels.The variable flow control valve of other kind also can be used for identical function.

Figure 16 also discloses controller 1640.Controller 1640 controls the operation of feedback valve 1618 and cold start-up valve 1620.Controller 1640 operates the air quantity to flow through feedback valve 1618 under the different situation of optimization.As described above, the air quantity flowing through feedback valve 1618 obtains special required minimum air flow amount required for situation.There is the special state of two kinds of its middle controller 1640 operational feedback valves 1618, described situation is: the low rpm, the high capacity that 1) surge limit of the compressor of given boosting demand are similar to motor; With 2) temperature of gaseous mixture is similar to the turbine 1606 entered under high rpm high load condition.

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

About controlling the temperature being supplied to the gaseous mixture of turbine 1606 under high speed, high load condition, the temperature limiting of gaseous mixture is extremely maximized the temperature of the operation of turbine 1606 by controller 1640, and can not the high mechanism that must damage turbine 1606.In one embodiment, the temperature of about 925 ° of C is optimum temperatures of gaseous mixture operation turbine 1606.Once the temperature being supplied to the gaseous mixture of turbine 1606 begins to exceed 900 ° of C, the pressurized air that so feedback valve 1618 is opened to allow since compressor 1608 cooled the thermal exhaust from catalytic type diesel particulate filter 1616 before penetrating turbine 1606.The temperature that controller 1640 can be designed to about 925 ° of C is 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 the temperature using traditional material that the damage to turbine 1606 may occur.Certainly, depend on the Special Category of assembly and the material used in turbine 1606, described controller can be designed to other temperature.Conventional proportional-integral-derivative (PID) control logic device can be used in controller 1640 to produce these controlled results.

The benefit controlling to enter the temperature of the gaseous mixture of turbine 1606 is to eliminate in exhaust, uses fuel to limit the turbine-entry temperature of gaseous mixture.The thermal exhaust using stream of compressed air of comparatively colding pressing to cool from catalytic type diesel particulate filter 1616 needs large quantity of air, and this comprises large quality to reach the required colder temperature of gaseous mixture.Cool from the air quantity needed for the thermal exhaust of catalytic type diesel particulate filter 1616 very large, this is because from compressor 1608 compared with cold compression air and the freezing mixture of non-good, especially with when injecting compared with the liquid fuel that is vented.Thermal exhaust from the output terminal of catalytic type diesel particulate filter 1616 causes comparatively cold compression gas expansion from compressor 1608 to produce gaseous mixture.Need to reduce from the temperature of the thermal exhaust of catalytic type diesel particulate filter 1616 compared with cold compression air due to the large quality from compressor 1608, so the gas and vapor permeation logistics of large quality flows through turbine 1606, which greatly enhances the output of turbine 1606.Turbo-power reason mass flow deducts compression and flows through the differential force of the differential generation of the merit needed for pressurized air of feedback valve 1618 and improve.By obtaining temperature of gas mixture signal 1630 from temperature transducer 1638 and controlling compressed-air actuated interpolation by feedback valve 1618, just maximum temperature can not be exceeded.

Controller 1640 also controls the surge that feedback valve 1618 comes in limit compression device 1608.Surge limit is along with boosting, is changed and the boundary of change by the air stream of compressor and the design of compressor 1608.When intake air 1622 stream is low and pressure ratio between intake air 1622 and pressurized air is high, in turbosupercharger, normally used compressor (such as compressor 1608) exceedes surge limit.In conventional Super turbosupercharger, when engine speed (rpm) 1626 is low, intake air 1622 flows for low.At low rpm, when motor 1602 does not use pressurized air in a large number, the mass flow of intake air 1622 is low and because air cannot be pushed in high-pressure conduit when flowing without rational intake air 1622 by rotary compressor 1608, and surge occurs.Feedback valve 1618 is allowed stream through air-pressure duct 1609 and is prevented or reduce the surge in compressor 1608.Once there is surge in compressor 1608, the pressure in air-pressure duct 1609 so cannot be kept.Therefore, under the low rpm, high capacity serviceability of motor 1602, the compressed-air actuated pressure in air-pressure duct 1609 can be reduced to desired level down.By opening feedback valve 1618, the intake air 1622 increased through compressor 1608 flows, and especially under the low rpm, high capacity serviceability of motor 1602, this allows reach required boost level in air-pressure duct 1609.Feedback valve 1618 can be opened simply until reach required pressure in air-pressure duct 1609.But, by detecting the boosting in air-pressure duct 1609 simply, open feedback valve 1618 make compressor 1608 avoid surging condition before will there is surge.

But, preferably before generation surging condition, measure surge limit and open feedback valve 1618 in advance.For given rpm and required boost level, surge limit can be measured.Feedback valve 1618 can start to open before compressor 1608 reaches calculating surge limit.Previously open described valve and allow that compressor upwards rotates quickly to higher boosting, this is because described compressor is closer to the greater efficiency point of compressor operation parameter.Then the rapid pressure risen under low rpm can be realized.By there is valve described in the front opening of surge, more stable control system can also be realized.

With a kind of make the mode of response improving motor 1602 open feedback valve 1618 time by allowing that motor 1602 reaches higher boosting to realize more quickly when motor 1602 is in lower rpm.Compressor 1608 is also more effective, and this causes the less merit of gearbox 1610 to realize super supercharging.Surge limit controls to be molded in the mode standard based on control simulation code, such as MATLAB.Be molded the autocoding of the algorithm of the simulation and controller 1640 of allowing controller 1640 by this way.

Pattern described above based on control system is unique, because use gearbox 1610 to control the rotation of turbine 1606 and compressor 1608 produce boosting and without turbo lag.In other words, gearbox 1610 can from arbor 1612 extract rotation can drive compressor 1608 and very fast and turbine 1606 produce enough mechanical energy with this desired level driving compressor 108 before air-pressure duct 1609, reach required boosting.In this way, reduce or eliminate in conventional turbocharger and reduce sluggish control piece.Pattern based on the control of controller 1640 should be designed to the optimum efficiency of compressor 1608 is remained in the operating parameter of compressor 108.

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

During the serviceability of motor 1602, wherein compressor 1608 keep off surge limit and as by temperature transducer 1638 detect the temperature not reaching gaseous mixture, system when feedback valve 1618 is closed carrys out work as the turbo charged system of conventional Super.This occurs on most of operating parameter of motor 1602.When there is the high capacity of motor 1602 and low rpm state, feedback valve 1618 is opened to prevent surge.Similarly, under the high rpm, high capacity serviceability of motor 1602, in the exhaust of the output terminal of catalytic type diesel particulate filter 1616, produce high temperature, therefore feedback valve 1618 must be opened to make the temperature of the fuel mixture being applied to turbine 1606 be reduced to the temperature that cause damage lower than meeting 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 comprises as provided the total efficiency higher than the turbo charged motor of conventional Super about the super-turbocharger be modified described by Figure 16 above, and provides height, optimum efficiency and the high rpm in low rpm, high capacity serviceability, height, the optimum efficiency under high load condition.Super-turbocharger comprises and is connected to the turbine 1606 of compressor 1608 by shaft mechanical.Compressor 1608 compresses intake air 1622 and compression intake air is supplied to conduit 1704.Conduit 1704 is connected to feedback valve 1618 and interstage cooler 1614.Disclosed in above, interstage cooler 1614 is used for cooling the pressurized air of heating during compression process.Interstage cooler 1614 is connected to air-pressure duct 1726, and air-pressure duct 1726 is then connected to the inlet manifold (not shown) of motor 1602.Pressure transducer 1636 is connected to air-pressure duct 1704 and carrys out detected pressures and compressed air pressure signal 1632 supply pressure reading by being applied to controller 1640.Disclosed in above, feedback valve 1618 is controlled by the controller feedback valve control signal 1642 produced by controller 1640.Under some serviceability, feedback valve 1618 is opened and pressurized air is supplied to mixing chamber 1706 from air-pressure duct 1704.

As 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 surrounded by air-pressure duct 1704 simply, and the pressurized air supplied from air-pressure duct 1704 is mixed with the exhaust catalytic type diesel particulate filter output duct 1708 through opening 1702.The mixing chamber of any required kind can be used to mix the temperature reducing described exhaust compared with 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 signal 1630 to controller 1640, controller 1640 controls feedback valve 1618 to guarantee that the temperature of the exhaust in 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 by catalytic type diesel particulate filter entry conductor 1714.By orientating as close to gas exhaust manifold 1710 by catalytic type diesel particulate filter 1616, the thermal exhaust from motor is flowed directly in catalytic type diesel particulate filter 1616, and this contributes to starting catalytic type diesel particulate filter 1616.In other words, close to the proximal most position of the outlet of engine exhaust, catalytic type diesel particulate filter 1616 does not allow that described exhaust cooled in fact before entering catalytic type diesel particulate filter 1616, which increase the performance of catalytic type diesel particulate filter 1616.When described exhaust is through catalytic type diesel particulate filter 1616, catalytic type diesel particulate filter 1616 is that described exhaust increases additional heat.These very hot exhausts of the output terminal of catalytic type diesel particulate filter 1616 are provided to catalytic type diesel particulate filter output duct 208 and are used in mixing chamber 1706 from the compression inlet air cooling of air-pressure duct 1704.Depend on the temperature of the very hot exhaust produced at the output terminal of catalytic type diesel particulate filter 1616, it changes according to the serviceability of motor 1602, and during high speed, high load condition, the compression intake air of different amount will be added in described exhaust.During low engine speed, engine high load state, feedback valve 1618 is also in order to allow that intake air flows through compressor to avoid surge.Surge is similar to the aerodynamic force stall of compressor blade, and this owing to occurring through the low stream mode of compressor during low engine speed state.But when there is surge, the pressure drop in inlet manifold (not shown), this is because compressor 1608 cannot compress intake air.By allowing that air flows through compressor 1608 owing to opening feedback valve 1618, can keeping the pressure in inlet manifold, making when needing high moment of torsion under low engine speed, described high moment of torsion can be achieved due to high inlet manifold pressure.

Disclosed in above, when motor operates under high speed, high load condition, catalytic type diesel particulate filter 1616 causes in the exhaust being provided to catalytic type diesel particulate filter output duct 1708 and produces amount of heat.By supply compression, colder intake air to catalytic type diesel particulate filter output duct 1708, the thermal exhaust at a high speed, under high load condition is cooled.When load and the speed raising of motor, produce hotter gas and need the more pressurized air from conduit 1704.Enough rotate can drive compressor if turbine 1606 does not provide, such as under low speed, high load condition, so engine crankshaft 1612 can supply rotation by rotating band 1722, drive pulley 1718, axle 1724, continuous variable gearbox 1716 and gearbox 1728 can to compressor 1608.Moreover, can use and advance any part of system can to compressor 1608 to supply rotation, and Figure 17 be open carries into execution a plan according to one of an open embodiment.

Equally as shown in Figure 17, cold start-up valve 1620 is also 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 in catalytic type diesel particulate filter 1616 upstream.Disclosed in above, the object of cold start-up valve provides compression intake air to the input end of catalytic type diesel particulate filter 1616 in the start-up conditions.In the start-up conditions, before catalytic type diesel particulate filter 1616 reaches full operation temperature, extra oxygen is provided to start catalytic process by cold start-up conduit 1712.The described extra oxygen provided by cold start-up conduit 1712 contributes to the beginning of catalytic process.Controller 1640 responding engine rate signal 1626, engine loading signal 1628 and temperature of gas mixture signal 1630 control cold start-up valve 1620 by controller cold start-up valve control signal 1644.

Therefore, efficient, super turbo charged motor 1600 operates in the mode being similar to super-turbocharger, except feedback valve 1618 because a compressed-air actuated part to be supplied to from compressor except the input end of turbine by two reasons.A reason before exhaust enters turbine, cools described exhaust make can use whole energy of described exhaust and do not need waste gas gate under high speed, high load condition.Another reason is to provide air stream through compressor to prevent the surge under low rpm, high load condition.In addition, before exhaust arrives turbine, catalytic type diesel particulate filter can connect within an exhaust-gas stream, make the heat produced by catalytic type diesel particulate filter 1616 can be used for driving turbine 1606, and the compression intake air mixed with the hot gas from catalytic type diesel particulate filter 1616 is expanded, which greatly enhances the efficiency of system.In addition, cold start-up valve 1620 can be used for by provide during starting state oxygen to exhaust the catalytic process that starts in catalytic type diesel particulate filter 1616.

Therefore, disclose unique super-turbocharger that a kind of use has the high speed traction driving of fixed ratio, the rotating machinery speed of turbine/compressor axle is reduced to the rpm level that can be used by the continuous variable gearbox of coupling energy between propelling system with turbine/compressor axle by described fixed ratio.The uniqueness of described super-turbocharger design is that gearbox is arranged in system.Described continuous variable gearbox is arranged in the lower part of super-turbocharger shell.Continuous variable gearbox 1116 is provided in the stepless variable velocity ratio transmitted between super-turbocharger and motor needed for rotating mechanical energy.Arbitrary gear continuous variable gearbox can be used as continuous variable gearbox 1116 maybe can use traction-driven continuous variable gearbox.Therefore, traction drive may be used for both high speed traction driving 114 and continuous variable gearbox 1116.

For the purpose of illustration and description presents aforementioned description of the present invention.And be not intended to detailed or limit the invention to disclosed precise forms, and other modifications and changes can be had according to above-mentioned teaching.Embodiment selects to explain principle of the present invention and its practical application best and describe, and others skilled in the art can be allowed thus to use the present invention best with the various embodiment and various modification that are suitable for the specific use of expecting.Claim of enclosing is intended to the scope be interpreted as except being limited to prior art, also comprises other alternate embodiment of the present invention.

Claims

1. be coupled to a super-turbocharger for motor, it comprises:

Turbine, it produces turbine rotating mechanical energy by the exhaust enthalpy produced by described motor;

Compressor, its compression sucks air and responds the described turbine rotating mechanical energy that produced by described turbine and be sent to described motor and from the engine revolution mechanical energy that described motor transmits, pressurized air be supplied to described motor;

Axle, it has the end being connected to described turbine and described compressor, and has the central part of axle traction surface;

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

Multiple planet rolling barrel, it has multiple planet rolling barrel traction surface, and described planet rolling barrel traction surface and described axle traction surface circle connect and make to there is multiple first traction interface between described multiple planet rolling barrel traction surface and described axle traction surface;

Circular-cylindrical, it is rotated by multiple second traction interface by described multiple planet rolling barrel;

Continuous variable gearbox, it is mechanically coupled to described traction drive and described motor, and turbine rotating mechanical energy is sent to described motor and under the service speed of described motor, engine revolution mechanical energy is sent to described traction drive by it.

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

3. super-turbocharger according to claim 2, wherein said continuous variable gearbox comprises planetary ball bearing traction drive continuous variable gearbox.

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

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

6. super-turbocharger according to claim 4, wherein said planet traction drive has the planet carrier it being provided with described planet rolling barrel.

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

8. super-turbocharger according to claim 6, wherein said circular-cylindrical has circular-cylindrical traction surface, and described circular-cylindrical traction surface and described multiple planet rolling barrel traction surface circle connect to set up described multiple second traction interface.

9. super-turbocharger according to claim 7, wherein said circular-cylindrical has multiple extra planet rolling barrel traction surface circle being less than described multiple planet rolling barrel traction surface with diameter and fetches the circular-cylindrical traction surface setting up described multiple second traction interface.

10. between super-turbocharger and motor, transmit a method for rotating mechanical energy, it comprises:

In turbine, turbine rotating mechanical energy is produced by the exhaust enthalpy produced by described motor;

Use compressor compresses suction air responds the described turbine rotating mechanical energy produced by described turbine and pressurized air is supplied to described motor by the engine revolution mechanical energy produced by described motor;

There is provided axle, it has the end being connected to described turbine and described compressor, and has the central part of axle traction surface;

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

Multiple planet rolling barrel traction surface of placing multiple planet rolling barrel make it contact described axle traction surface to make to set up multiple first traction interface between described multiple planet rolling barrel traction surface and described axle traction surface;

Place circular-cylindrical to make it contact described multiple planet rolling barrel to make to set up multiple second traction interface between described multiple planet rolling barrel and described circular-cylindrical;

Continuous variable gearbox be mechanically coupled to described traction drive and described motor and under the service speed of described motor, described turbine rotating mechanical energy be sent to described motor and under the service speed of described compressor and described turbine, engine revolution mechanical energy be sent to described axle.

11. methods according to claim 10, the process wherein transmitting rotating mechanical energy between described super-turbocharger and described motor comprises and transmits rotating mechanical energy by least one mechanical device.

12. methods according to claim 11, are wherein comprised by the described process of at least one mechanical device transmission rotating mechanical energy and transmit rotating mechanical energy by the gearbox of vehicle.

13. methods according to claim 11, are wherein comprised by the described process of at least one mechanical device transmission rotating mechanical energy and transmit the propelling system of rotating mechanical energy to vehicle.

14. methods according to claim 10, wherein place described circular-cylindrical and its process contacting described multiple planet rolling barrel is comprised:

The circular-cylindrical traction surface of placing described circular-cylindrical makes it contact described multiple planet rolling barrel traction surface to set up described multiple second traction interface.

15. methods according to claim 10, wherein place described circular-cylindrical and its process contacting described multiple planet rolling barrel is comprised:

The circular-cylindrical traction surface of placing described circular-cylindrical makes its contact diameter be less than the multiple extra planet rolling barrel traction surface of described multiple planet rolling barrel traction surface to set up described multiple second traction interface.

16. methods according to claim 10, are wherein mechanically coupled to described traction-driven process and comprise by continuous variable gearbox:

Traction drive continuous variable gearbox is mechanically coupled to described traction drive.

17. methods according to claim 16, are wherein mechanically coupled to process described in described traction-driven by traction drive continuous variable gearbox and comprise:

The continuous variable gearbox of planetary ball bearing is mechanically coupled to described traction drive.

18. methods according to claim 16, the described process wherein traction drive being mechanically coupled to described axle traction surface comprises:

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

19. 1 kinds of methods transmitting rotating mechanical energy under the various operational conditions of motor between super-turbocharger and the propelling system being coupled to described motor, it comprises:

Use compressor compresses to suck air and respond the described turbine rotating mechanical energy that produced by described turbine and propelling is that pressurized air is supplied to described motor by rotating mechanical energy;

There is provided the axle with traction surface, described shaft mechanical is coupled to described turbine and described compressor;

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

Mechanically be coupled gearbox between described traction drive with described propelling system, with described turbine rotating mechanical energy is sent to described propelling system and be that rotating mechanical energy is sent to described compressor by propelling.

20. methods according to claim 19, wherein between described traction drive and described propelling system, the process of mechanical coupling gearbox comprises:

Mechanically be coupled gearbox between described traction drive with described engine crankshaft, described turbine rotating mechanical energy being sent to described arbor under the various operational conditions of described motor and be that mechanical energy is sent to described compressor by propelling.

21. methods according to claim 19, the process wherein transmitting rotating mechanical energy between described super-turbocharger and described propelling system comprises and transmits rotating mechanical energy by least one mechanical device.

22. methods according to claim 21, are wherein comprised by the described process of at least one mechanical device transmission rotating mechanical energy and transmit rotating mechanical energy by the gearbox of vehicle.

23. methods according to claim 21, are wherein comprised by the described process of at least one mechanical device transmission rotating mechanical energy and transmit the propelling system of rotating mechanical energy to vehicle.

24. methods according to claim 19, are wherein mechanically coupled to described traction-driven process and comprise by gearbox:

Continuous variable gearbox is mechanically coupled to described traction drive.

25. 1 kinds of super-turbocharger being coupled to motor, it comprises:

Axle, it connects described turbine and described compressor and has axle traction surface;

Traction drive, it has the traction drive surface connect with described axle traction surface circle;

Electrical motor generator, it is mechanically coupled to described traction drive indirectly, makes turbine rotating mechanical energy be transferred into described electrical motor generator and electrical motor generator rotating mechanical energy is transferred into described traction drive.

26. 1 kinds of super-turbocharger being coupled to motor, it comprises:

Gearbox, it is mechanically coupled to described traction drive and described motor, and turbine rotating mechanical energy is sent to described motor and engine revolution mechanical energy is sent to described traction drive by it.

27. super-turbocharger according to claim 26, wherein said gearbox comprises automatic gearbox.

28. 1 kinds of super-turbocharger being coupled to motor, it comprises:

Hydraulic gearbox, it is mechanically coupled to described traction drive and described motor, and turbine rotating mechanical energy is sent to described motor and engine revolution mechanical energy is sent to described traction drive by it.

29. 1 kinds during the various operational conditions of motor, between super-turbocharger and motor, transmit rotating mechanical energy and transmit its energy to advance system and be energy-delivering method from propelling, it comprises:

There is provided the axle with traction surface, described axle is coupled to described turbine;

Electrical motor generator is mechanically coupled to indirectly described traction drive described turbine rotating mechanical energy is sent to described electrical motor generator and electrical motor generator rotating mechanical energy is sent to described traction drive.

30. 1 kinds of methods transmitting rotating mechanical energy during the various operational conditions of motor between super-turbocharger and described motor, it comprises:

Between described traction drive and described motor by automatic gearbox gearbox mechanical coupling described turbine rotating mechanical energy is sent to described motor and engine revolution mechanical energy is sent to described traction drive.

31. 1 kinds of methods transmitting rotating mechanical energy during the various operational conditions of motor between super-turbocharger and described motor, it comprises:

Between described traction drive and described motor by hydraulic gearbox mechanical coupling described turbine rotating mechanical energy is sent to described motor and engine revolution mechanical energy is sent to described traction drive.

32. 1 kinds of methods transmitting rotating mechanical energy during the various operational conditions of motor between super-turbocharger and described motor, it comprises:

Between described traction drive and described motor by self-shifting manual transmission mechanical coupling described turbine rotating mechanical energy is sent to described motor and engine revolution mechanical energy is sent to described traction drive.