WO1998029647A1 - Moteur suralimente hybride - Google Patents
Moteur suralimente hybride Download PDFInfo
- Publication number
- WO1998029647A1 WO1998029647A1 PCT/JP1997/004768 JP9704768W WO9829647A1 WO 1998029647 A1 WO1998029647 A1 WO 1998029647A1 JP 9704768 W JP9704768 W JP 9704768W WO 9829647 A1 WO9829647 A1 WO 9829647A1
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- WIPO (PCT)
- Prior art keywords
- engine
- pressure
- speed
- positive displacement
- hybrid
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/04—Mechanical drives; Variable-gear-ratio drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/12—Drives characterised by use of couplings or clutches therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/32—Miller cycle
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a supercharging system for an engine, particularly a turbocharger (hereinafter, referred to as TC) as a supercharger.
- TC turbocharger
- the invention relates to a hybrid supercharged engine in which the engine is arranged in series with a TC and supercharges the engine in two stages, and also relates to an improvement of Patent Application No. 3588847 of 1996. Background art
- the TC is a speed type and has the characteristics shown in FIG. 2, (a) a vehicle that requires a low-speed torque due to the characteristic of increasing the pressure ratio (hereinafter referred to as pressure) in proportion to the rotation speed and the flow rate at the TC.
- pressure the pressure ratio
- the operating line is changed to the line a-1b in Fig. 2.
- the low-speed torque is insufficient compared with the unsupercharged engine, and the vehicle engine is especially required to start from stop and accelerate (hereinafter referred to as zero start). Insufficient ability.
- the TC operating line a — b shown in Figure 2 is the highest efficiency curve. c-d only intersects at point r, and the fuel consumption rate (hereinafter referred to as BSFC) is low near point r in Fig. 3, which corresponds to point r in Fig. 2, but other engine operating conditions , The TC efficiency is low and the BSFC cannot be low.
- BSFC fuel consumption rate
- the BSFC of the engine approaches the indicated fuel consumption rate (hereinafter referred to as ISFC) indicated by the dashed line e-f with the increase of BMEP, and then decreases. .
- ISFC indicated fuel consumption rate
- TC supercharged Susumuru supercharged vehicle engine line a- b in FIG. 3 for example, increase the performance up to 1 6 kg / cm 2 BME P, Doo-out its
- the BSFC can be set at 140 g / ps-hr, as shown by point a in Fig. 5, but in the g zone in Fig. 3, the engine load is about 1-4.
- the BSFC at this time increases from the force in Fig. 5 to the point t and ZOOgZps_hr.
- the BMEP can be further increased to, for example, 32 kg Z cm 2 at point j in FIG. 5 and twice as much as the TC supercharged engine
- the BSFC under 1/4 load can be increased to 200 g at point t. From / ps — hr, it is possible to obtain 1 55 g / ps — hr at point i.
- the current TC supercharged engine should further increase the BMEP, which reduces the BSFC. If the output is the same, there is a demand for a smaller, lighter and cheaper engine. However, it is not possible for the reasons mentioned above.
- a further factor preventing the widespread use of TC supercharged engines is turbo lag.
- the speed of the TC of the engine in the idle state when the vehicle is stopped is about 500 rpm, and it is required that the TC be accelerated to about 50,000 rpm with the acceleration of the vehicle. Therefore, the TC does not have any supercharging function during zero-start acceleration, and the vehicle is forced to perform zero-start acceleration while maintaining the performance at the time of no supercharging as shown by the lines c-d in Fig. 3. It becomes.
- the compression ratio of a diesel engine is generally determined in consideration of the starting performance, and a decrease in the compression ratio makes it difficult to start the engine.
- Starting aids such as glove lugs are useful for starting the engine, but are not useful for preventing the emission of white smoke containing toxic substances such as formaldehyde immediately after starting.
- TC supercharged engines are struggling with starting measures.
- the present invention has been made to solve the above problems.
- a first object of the present invention is to provide a low-speed torque, sufficient zero-start capability when mounted on a vehicle, a medium-speed torque without sacrificing the maximum output, a small turbo lag, and low fuel consumption.
- An object of the present invention is to provide a hybrid supercharged engine having excellent performance.
- a second object of the present invention is to provide a hybrid supercharged engine capable of achieving not only a fool that can achieve a low BSFC but also a BMEP that is at least twice as large as a TC supercharged engine. It is here.
- a third object of the present invention is to increase the amount of air supplied to the engine by supercharging mainly at the time of low speed and increasing the TC at low speeds, thereby increasing the TC to reduce the speed at low speeds without generating turbo lag.
- An object of the present invention is to provide a hybrid supercharged engine that can exhibit performance during steady operation even during rapid acceleration.
- a fourth object of the present invention is to provide a high-priority engine that enables the SC to function effectively even at the time of starting, raises the compression pressure and temperature of the engine, and facilitates the starting of a high-ratio output engine, which must have a low compression ratio. To provide a supercharged engine.
- a fifth object of the present invention is to reduce the NOx emission without sacrificing the reliability of the engine as well as making it possible to reduce the size, weight and cost of the engine.
- Another object of the present invention is to provide a hybrid supercharged engine having an effect of reducing the power consumption. Disclosure of the invention
- the hybrid supercharged engine of the present invention includes a turbocharger having a maximum capacity at a speed higher than the maximum torque rotation speed of the engine, and a positive displacement turbocharger installed in series with the turbocharger. It is characterized in that two-stage supercharging is performed while controlling the feeder to keep the air supply constant regardless of the engine speed. Thereby, the above-mentioned plurality of objects can be achieved.
- the present invention provides a method of controlling the amount of air supplied from the positive displacement supercharger to a bypass valve provided in the bypass provided on the positive displacement supercharger side and a supply flow meter provided in conjunction with the valve.
- the bypass valve in the bypass provided on the mold supercharger side and the tachometer provided on the supercharger are respectively adjusted. Thereby, the adjustment of the air supply amount can be performed accurately.
- the present invention provides the above-described hybrid supercharged engine, wherein an air supply pressure gauge provided in an air supply system thereof and a bypass valve provided in a bypass provided in a positive displacement supercharger side are provided.
- the maximum supply pressure is adjusted so that the maximum pressure does not exceed the maximum allowable pressure of the engine. As a result, the maximum supply pressure can be obtained within a range not exceeding the allowable maximum pressure of the engine.
- the hybrid supercharged engine includes a mirror-cycle system capable of obtaining a high expansion ratio, and the internal pressure of the cylinder does not exceed the maximum allowable pressure of the engine.
- the compression ratio is characterized by controlling the compression ratio to be low and maintaining a low fuel consumption rate.
- the compression ratio can be reduced to suppress the maximum allowable pressure of the engine, and to achieve a low fuel consumption rate.
- the present invention is configured such that the positive displacement supercharger is driven via a slip clutch, and the clutch is connected to the air supply pressure gauge and the air supply flow meter to reduce the slip rate. It is characterized by controlling the supply pressure and the supply flow rate to the engine by changing the control. This makes it easier to adjust the positive displacement turbocharger.
- the present invention is configured such that the positive displacement supercharger is driven via a continuously variable transmission, and the transmission is controlled so as to change a rotation ratio between an engine and a positive displacement supercharger, Wenge It is characterized by adjusting the air supply pressure and the same flow rate. This makes it easier to adjust the positive displacement supercharger.
- the present invention is configured such that the positive displacement supercharger is driven via a differential gear mechanism, and the differential gear mechanism is controlled by the air supply pressure gauge, the flow meter and the pressure regulating valve. It is characterized by adjusting the supply pressure and supply flow rate to the engine. This makes it easier to adjust the positive displacement turbocharger.
- the present invention reduces the volumetric supercharger and when I cormorant configuration to by-powered spark ignition engine monitor, an exhaust gas recirculation the ⁇ flowers ignition engine (EGR) control to NO x This is the feature. This makes it easier to adjust the positive displacement turbocharger.
- EGR exhaust gas recirculation the ⁇ flowers ignition engine
- the present invention is characterized in that the positive displacement supercharger is a speed supercharger.
- the speed-type supercharger contributes to the achievement of the above-mentioned plurality of objects similarly to the positive-displacement type supercharger.
- Fig. 1 is an overall configuration diagram showing an example of the engine of the present invention
- Fig. 2 is a diagram showing TC flow rate vs. pressure ratio
- Fig. 3 is a diagram showing engine speed and torque and supply pressure ratio diagram
- Fig. 4 Fig. 5 shows the relationship between engine load and supply pressure ratio
- Fig. 5 shows the relationship between engine supply pressure ratio and fuel efficiency
- Fig. 6 shows the p-V diagram of the mirror cycle
- Fig. 7 shows , Engine valve opening / closing diagram
- FIG. 8 is a cycle diagram
- FIG. 9 is a schematic diagram of a charge air cooler
- FIG. 10 is a schematic configuration diagram showing a first application example of the present invention
- FIG. FIG. 1 is a schematic configuration diagram showing a second application example of the present invention
- FIG. 12 is a schematic configuration diagram showing a third application example of the present invention.
- FIG. 1 shows an example of the hybrid supercharged engine of the present invention.
- the pulley 3 is fixed to the tip 2 of the crankshaft of the engine 1 and the belt 4 is fixed to the drive shaft 6 of the SC 5.
- the SC 5, which is driven by the engine 1, sucks the air through the intake pipe 8, compresses it, passes through the discharge pipe 9, and cools the TC 10 through the air supply cooler 11.
- the air is supplied to the engine 10a, compressed further by the TC 10 and increased in pressure, and is supplied to the engine 1 through the air supply pipe 13 and the air supply cooler 12.
- the air supply pipe 13 is provided with a pressure sensor 21 for transmitting the air supply pressure to the electronic controller 17.
- Reference numeral 5a denotes an SC rotation speed sensor attached to the drive shaft 6 of the SC 5, which is connected so as to transmit the rotation speed of the SC 5 to the electronic controller 17.
- the exhaust of Engine 1 drives the turbine 10b of the exhaust manifold TC10 14 and is discharged to the exhaust side of the exhaust pipe 15 and the power of the turbine 10b is driven by the shaft 10c.
- the compressor 10a is driven.
- the rotational speeds of the turbine 10b and the compressor 10a are detected by a TC rotational speed sensor 10d attached to the shaft 10c, and transmitted to the electronic controller 17. .
- a flow meter 16 is provided in the intake pipe 8
- a cooling water temperature sensor 24 is provided in the cooling water of the engine 1
- an engine speed sensor 25 is provided at the tip 2 of the crankshaft, and an accelerator pedal 2 for controlling the operating state of the engine 1.
- 2 is provided with a position sensor 23 for controlling the load of the driver, and each of them is transmitted to the electronic controller 17, and the controller 17 determines the control amount, and determines the control amount.
- the opening of the bypass valve 20 provided in the bypass 19 is controlled by the actuator 18.
- the cooling water temperature sensor 24 installed in the cooling water jacket of the engine 1 indicates the cooling water temperature of the engine 1
- the engine speed sensor 25 indicates the rotation speed of the tip 2 of the crank shaft of the engine 1.
- the pollution level of exhaust gas is low.
- TC 10 of engine 1 increases the pressure ratio along with the maximum flow rate along the maximum efficiency line c 1 d of the performance curve in FIG.
- Engine 1 can The line a-h is supercharged by the air supply at a pressure ratio of h, and the performance shown by the corresponding torque curve is obtained.
- the torque curve indicated by the lines a to h indicates an operating state in which the bypass valve 20 is fully opened and the SC 5 does not increase the air supply amount and the pressure ratio in the engine of the present invention.
- the vehicle's running resistance curve is also almost the same as the line a-h.
- the TC supercharged engine tuned as described above is further equipped with an SC installed in series with the TC to increase the air supply pressure ratio and ⁇ ⁇ ⁇ Increase the air supply flow rate.
- the flow rate and the pressure ratio of the TC 10 are point d in FIG. 2, but the characteristics of TC are the same, while maintaining the pressure ratio at the point d. If the flow rate is increased, the point d will exceed the speed limit line i_g in Fig. 2, and the centrifugal force may damage the rotor (not shown). . Also, decreasing the flow means that point d is to the left of the surging limit line h—f, and TC loses its function.
- the supply air pressure ratio and the flow rate generated by SC5 are adjusted so as to maintain the point d in FIG.
- the pressure sensor 21 provided in the air supply pipe 13 allows the supply pressure to be electronically controlled so that the supply pressure ratio does not exceed 6, for example.
- the controller 17 instructs the actuator 18 to adjust the degree of opening of the bypass valve 20 so that the supply air pressure ratio is kept constant, thereby controlling the engine 1.
- the generated torque is set to a value corresponding to point m in FIG.
- FIG. Figure 4 shows the supply pressure from no load to full load. That is, the point n in FIG. 4 is when there is no load.
- the accelerator pedal 22 in FIG. 1 is in the position indicated by the solid line, and the position sensor 23 is informed to the electronic controller 17 that there is no load.
- the controller 17 commands the actuator 18 to open the bypass valve 20 fully. Therefore, SC 5 does not function, and the atmosphere is supplied to engine 1 via intake pipe 8, bypass 19, discharge pipe 9, TC 10 and air supply pipe 13 and TC 10 is supplied with air in this state.
- the atmospheric pressure that is, the pressure ratio, remains at 1 without increasing the pressure ratio.
- the position sensor 2 3 Communicates its position to the electronic controller 17 which still instructs the actuator 18 to keep the bypass valve 20 fully open. Therefore, at point i in FIGS. 4 and 3, the supercharging is performed only by the TC 10, and the exhaust gas temperature rises due to the increase in the fuel supply amount.
- the engine 1 uses the air supply pressure to generate a higher torque, point i, than the point P in the case of no supercharging in Fig. 3.
- the position sensor 23 transmits the position to the electronic controller 17, and the controller 17 transmits the position to the actuator.
- the controller 17 transmits the position to the actuator.
- the accelerator pedal 22 is depressed to the position shown by the dotted line in Fig. 1, the fuel supply is maximized, and the position sensor 23 informs the electronic controller 17 of it. Commands the actuator 18 to rotate the bypass valve 20 further in the closing direction and reduce the flow rate of the bypass valve 20 backflow, thereby increasing the pressure in the discharge pipe and cooperating with the cutter C10. Therefore, the pressure inside the air supply pipe 13 is increased.
- the amount of intake air to the engine 1 is measured by the flow meter 16 and transmitted to the electronic controller 17 which controls the point in Fig. 2 where the air amount is the limit of TC10. Instruct the actuator 18 to adjust the opening area of the bypass valve 20 so as not to exceed d.
- the supply air pressure ratio at which TC 10 is generated is, for example, 3 and for the above-mentioned reason, the pressure ratio at the point ⁇ in FIG.
- the pressure ratio is adjusted to be 2.
- the torque curve of the hybrid supercharged engine of the present invention which is indicated by the line q--j-1h in FIG. 3, has several times the performance of the torque curve a--r-1b of the conventionally known TC supercharged engine.
- the vehicle engine emphasizes the torque at low speed, the engine speed must not exceed the maximum allowable pressure of engine 1, for example, even at an engine speed of 100 rpm or less. If it is possible to maintain the supply pressure ratio at full load as shown in Fig. 7, for example, 6, it is possible to obtain an ideal torque curve represented by the line m-j.
- a pressure sensor 21 is provided inside the air supply pipe 13 to measure the pressure inside the air supply pipe 13, and the pressure is transmitted to the electronic controller 17. Instruct the actuator 18 to adjust the opening area of the bypass valve 20 so that the line q—j in FIG. 3 is corrected to become the line m—j.
- the BSFC of the engine using the hybrid supercharging system of the present invention will be described.
- the BSFC is infinite when BMEP is zero.
- the BSFC when the engine of the present invention generates the torque at point j in FIG. 3 is represented by point i in FIG. 5.
- TC 10 operates at point d in FIG. Be oriented.
- the driving force of the mechanically driven SC 5 is added as the friction mean effective pressure FM EP, increasing the BSFC from point j in Fig. 5 to point ⁇ '.
- FM EP friction mean effective pressure
- the s zone in Fig. 3 which is about 1/4 of the load factor.
- the BSFC determines the fuel efficiency of the vehicle. is there. Entering this in Figure 5 gives the s zone.
- the maximum torque of a normal TC engine is point r in Fig. 3, and the frequently used zone is g. If this is entered in Fig. 5, the BSFC is in the g zone, and the difference in running fuel efficiency is clear when compared with the s zone in the engine of the present invention.
- an engine supplied with a high supply pressure reaching a pressure ratio of 6 has a point b at a normal compression ratio of 14 to 16 as shown by the solid line a—b in the p—V diagram of FIG.
- the compression pressure shown in Fig. 4 is high, and the combustion pressure also rises as high as line b-c-d, and exceeds the maximum allowable engine pressure shown in line e-f.
- lowering the compression ratio means either increasing the BSCFC, lowering the expansion ratio, increasing the exhaust temperature, and increasing the heat load of the engine.
- the expansion stroke is almost the same as the line d-m when the compression ratio is high, and the expansion ratio does not change even if the compression ratio is lowered, and the BSFC does not change.
- Licca The high expansion ratio also reduced the temperature of the exhaust gas.
- a rotary valve is provided in an intake passage of a known engine, and the closing timing of the rotary valve is set in the middle of the intake stroke, for example, by closing at a point g in FIG. Although it can be realized, it is also possible by the known "slow closing".
- Fig. 7 shows an example of this.
- the intake valve (not shown) opens at an angle of about 10 ° slightly before top dead center, and at an angle of about 30 ° after bottom dead center.
- intake starts at angle a, and the intake valve continues to open even after the bottom dead center and enters the compression stroke.
- the air continues to be discharged into the intake passage again after entering the compression stroke, and does not increase the cylinder pressure.
- the air intake valve closes when it reaches an angle c of about 70 ° after bottom dead center.
- FIG. 6 it becomes a point g, which is a substantial compression stroke, and can be a late-closed mirror cycle as described above.
- the engine of the present invention is required to have the highest BMEP near the maximum engine speed and does not require a high BMEP at low and medium speeds, the engine speed at point j in Fig. If the engine is tuned so that the maximum speed of the engine is, for example, 2 OOO rpm and the point d in Fig. 2, which is the maximum capacity of the TC, is the point h in Fig. 3, for example, 400 rpm, the above-mentioned reason can be obtained. Produces the best BMEP at the highest engine speeds.
- the speed is set at 200 rpm.
- this engine is maintained at a constant flow rate of TC, and the engine speed is further increased.
- the BMEP at the point t in FIG.
- the supply pressure at point h in Fig. 3 corresponds to the line a-b in Fig. 8.
- the engine starts intake from the top dead center of the intake stroke at point a, and the bottom dead. Near point b, the intake valve closes, starts the compression stroke from point b, reaches the top dead center at point c, burns and expands after increasing the pressure to line c 1 d 1 e.
- the exhaust valve opens at point f, but if the engine speed is increased as it is, the flow rate flowing through the TC increases, and the operating point of the TC rises beyond point d in Fig.
- the p-V diagram at this time is a line g-i-j-k-m-b.
- the BMEP drops to 1 / 1.25 at 2000 rpm and becomes the point t in Fig. 3.
- the engine of the present invention must also reduce the compression ratio, and it is necessary to deal with the startability, especially the starting at low temperature, by a new technology.
- the speed driven by a starter (not shown) at the time of starting is about 100 rpm, but this speed is measured by an engine speed sensor 2 provided at the tip 2 of the crank shaft. 5 and sends it to the electronic controller 17, which instructs the actuator 18 to fully close the bypass valve 20, which causes the SC 5 to adiabatically compress the intake air. Then, the pressure and temperature of the air in the discharge pipe 9 are increased.
- a bypass 26 is provided between the inlet and outlet of the supply air coolers 11 and 12, and a switching valve 27 is provided at the junction between the bypass 26 and the discharge pipe 9. So that the supply air is not cooled by the supply air coolers 11 and 12.
- the passage to the side 1 and 12 is closed and the passage to the bypass 26 is opened. That is, the cooling water temperature of the engine at the time of starting is low, and the cooling water temperature sensor 24 in FIG. 1 transmits the temperature to the electronic controller 17, and the controller 17 instructs the actuator 29 to return the temperature.
- the switching valve 27 is operated so as to close the passage of the discharge pipe 9 to the supply air coolers 11 and 12 and open the passage of the bypass 26.
- the compression temperature does not rise because the temperature of the engine cooling water is low, and the fuel burns incompletely and emits white smoke containing pollutants such as formaldehyde.
- the position sensor 23 informs the electronic controller 17 that the position of the accelerator pedal 22 is in the idle
- the low-temperature information from the cooling water temperature sensor 24 is used.
- the electronic controller 17 instructs the actuator 18 to close the bypass valve 20 and raises the compression temperature and pressure of the engine by increasing the pressure and temperature of the discharge pipe 9 by SC 5. It is.
- the pulley 7 drives the SC 5 instead of the pulley 7 side.
- a continuously variable transmission 30 (hereinafter referred to as a CVT) is provided between the shaft 6a of the SC 5 and the shaft 6b of the SC 5 side.
- the flow rate is measured by the flow meter 16 and transmitted to the electronic controller 17, which instructs the actuator 31.
- the SC 5 is driven while the rotation ratio between the drive shafts 6a and 6b is adjusted by the CVT 30.
- SC5 which is a positive displacement turbocharger having the characteristic that its rotation speed and the flow rate are directly proportional, can adjust the flow rate by adjusting its rotation speed, and the speed attached to the drive shaft 6 b It is also possible to measure the rotation speed of the SC 5 by the total 32 and transmit it to the electronic controller 17 to adjust the rotation speed of the SC 5.
- the pressure in the air supply pipe 13 is measured by the pressure gauge 21 so that the combustion pressure does not exceed the maximum allowable engine pressure.
- the controller 17 instructs the actuator 31 to adjust the speed of the SC 5 by means of the CVT 30.
- FIG. 11 shows an example in which a known differential supercharging method in which the SC is driven by a differential gear is applied to the hybrid supercharged engine of the present invention.
- SC5 is driven by a differential gear.
- the output of the engine 1 is provided on the output shaft 33, and the output shaft 33 is provided with the differential shafts 3 2a for driving the planetary gears 3 2b of the car 3 2
- the planetary gear 3 2b is fixed to the internal gear 3 2c and the sun gear 3 2d
- the internal gear 32 c is fixed to the drive shaft 34 and the vehicle wheels (shown in FIG. Drive).
- the planetary gear 3 2 b transmits the reaction force to the sun gear 3 2 d
- the gear 35 fixed to the sun gear 3 2 d transmits the SC drive gear 36 fixed to the drive shaft 6 of the SC 5.
- SC 5 is driven by Engine 1, usually 10% of engine torque.
- a feature of the differential gear mechanism is that the torque ratio transmitted to the drive shaft 34 and the sun gear 32d is constant, and drives the SC 5 when the torque of the drive shaft 34, that is, when the running resistance of the vehicle is large. And the SC5 increases the supply pressure according to the torque. In addition, the engine 1 generates high torque due to the supply pressure.
- the torque and the supply pressure become the line j-h in FIG. 3, and the intake air amount must be constant even if the engine speed changes. It must be measured by the flow meter 16 and transmitted to the electronic controller 17, which instructs the actuator 38, which opens the brake valve 37 fixed to the lever 39.
- the actuator 38 By adjusting the pressure and the pressure in the upstream portion 9a of the discharge pipe, the drive torque and the rotation speed of the SC 5 are adjusted to adjust the flow rate.
- the opening of the brake valve 37 the rotation speed of the SC 5 can be adjusted, and the flow rate flowing through the flow meter 16 can also be adjusted.
- the pressure of the pressure gauge 21 attached to the air supply pipe 13 is transmitted to the electronic controller 17, which instructs the actuator 18 to adjust the opening of the brake valve 37.
- the pressure in the discharge pipe 9 can be adjusted, and the torque represented by the line m_j in FIG. 3 can be generated in the engine 1.
- FIG. 5 is driven to draw air from the intake pipe 8 and increase the pressure in the discharge pipe 9 .
- the exhaust of the spark ignition engine 40 is a three-way catalyst 4 installed in the middle of the exhaust pipe 4 5. After being purified by the gas 6, it flows into the intake pipe 8 as EGR gas, is compressed by the SC 5, and is supplied to the engine 1 through the discharge pipe 9, TC 10 and the air supply pipe 13. You.
- the gas amount supplied to the engine 1, that is, the air amount + the EGR gas amount is changed even if the engine speed changes. It must be kept constant and measured by the flow meter 16 and transmitted to the electronic controller 17, which instructs the actuator 44, and the intake pipe of the spark ignition engine 40.
- the output of the spark ignition engine 40 is adjusted by adjusting the opening of the throttle valve 4 2 installed in 41, and the flow rate is adjusted by adjusting the rotation speed of the SC 5.
- the driver operates the accelerator pedal 22 according to the load of the engine 1, and the position sensor 23 transmits the position to the electronic controller 17, which controls the supply amount and pressure according to the load.
- the electronic controller 17 which controls the supply amount and pressure according to the load.
- the output is controlled by varying the rotation speed of the SC 5 for the supply flow rate and the input pressure to the engine 1 .
- SC 5 is a positive displacement supercharger
- the compressor of TC which is a speed supercharger
- SC5 is also a compressor that increases the flow rate and pressure as well as the rotational speed.
- the supercharger shown as SC5 in FIGS. 10 and 12 is not limited to a positive displacement type, but may be a speed type, for example, a centrifugal compressor (not shown). However, there is no problem with the function. ⁇
- the SC driven by the engine takes in the air and compresses it, supplies it to the TC compressor, further compresses it, raises the pressure, and passes the engine through the air supply pipe etc.
- the TC compressor driven by engine exhaust, draws in air and compresses it, which is then driven by engine power.
- the engine may be configured to be supplied to the SC, further compressed, increased in pressure, and supplied to the engine via an air supply pipe or the like. According to the inventors' research, it has been found that the latter has the advantage that the operation of TC is more stable and the SC can be made smaller than the former.
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69734530T DE69734530T2 (de) | 1996-12-27 | 1997-12-24 | Geladener hybridmotor |
US09/331,369 US6343473B1 (en) | 1996-12-27 | 1997-12-24 | Hybrid supercharged engine |
EP97949216A EP0957247B1 (en) | 1996-12-27 | 1997-12-24 | Hybrid supercharged engine |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8/358847 | 1996-12-27 | ||
JP35884796 | 1996-12-27 | ||
JP9345816A JPH10238354A (ja) | 1996-12-27 | 1997-11-30 | ハイブリッド過給エンジン |
JP9/345816 | 1997-11-30 |
Publications (1)
Publication Number | Publication Date |
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WO1998029647A1 true WO1998029647A1 (fr) | 1998-07-09 |
Family
ID=26578121
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1997/004768 WO1998029647A1 (fr) | 1996-12-27 | 1997-12-24 | Moteur suralimente hybride |
Country Status (5)
Country | Link |
---|---|
US (1) | US6343473B1 (ja) |
EP (1) | EP0957247B1 (ja) |
JP (1) | JPH10238354A (ja) |
DE (1) | DE69734530T2 (ja) |
WO (1) | WO1998029647A1 (ja) |
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CN106555684B (zh) * | 2015-09-29 | 2019-09-03 | 长城汽车股份有限公司 | 车辆、两级增压控制系统及其控制方法 |
US9797321B2 (en) * | 2016-02-09 | 2017-10-24 | GM Global Technology Operations LLC | Internal combustion engine with elevated compression ratio and multi-stage boosting including a variable-speed supercharger |
KR101956482B1 (ko) * | 2017-12-12 | 2019-03-08 | 한양대학교 산학협력단 | 전동 슈퍼차저를 장착한 하이브리드 차량의 동력 분배 방법 |
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1997
- 1997-11-30 JP JP9345816A patent/JPH10238354A/ja not_active Ceased
- 1997-12-24 WO PCT/JP1997/004768 patent/WO1998029647A1/ja active IP Right Grant
- 1997-12-24 EP EP97949216A patent/EP0957247B1/en not_active Expired - Lifetime
- 1997-12-24 US US09/331,369 patent/US6343473B1/en not_active Expired - Fee Related
- 1997-12-24 DE DE69734530T patent/DE69734530T2/de not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
---|---|
DE69734530D1 (de) | 2005-12-08 |
EP0957247A1 (en) | 1999-11-17 |
JPH10238354A (ja) | 1998-09-08 |
DE69734530T2 (de) | 2006-08-10 |
EP0957247B1 (en) | 2005-11-02 |
EP0957247A4 (en) | 2002-01-02 |
US6343473B1 (en) | 2002-02-05 |
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