WO2010128558A1 - Moteur présentant un détendeur volumétrique comme régénérateur - Google Patents

Moteur présentant un détendeur volumétrique comme régénérateur Download PDF

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Publication number
WO2010128558A1
WO2010128558A1 PCT/JP2009/058698 JP2009058698W WO2010128558A1 WO 2010128558 A1 WO2010128558 A1 WO 2010128558A1 JP 2009058698 W JP2009058698 W JP 2009058698W WO 2010128558 A1 WO2010128558 A1 WO 2010128558A1
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WIPO (PCT)
Prior art keywords
positive displacement
valve
expander
engine
exhaust
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PCT/JP2009/058698
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English (en)
Japanese (ja)
Inventor
和男 大山
Original Assignee
株式会社Joho
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Publication date
Application filed by 株式会社Joho filed Critical 株式会社Joho
Priority to PCT/JP2009/058698 priority Critical patent/WO2010128558A1/fr
Priority to PCT/JP2009/065202 priority patent/WO2010128567A1/fr
Publication of WO2010128558A1 publication Critical patent/WO2010128558A1/fr

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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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/06—Engines with prolonged expansion in compound cylinders

Definitions

  • the present invention relates to a partial efficiency improvement of a positive displacement engine provided with a positive displacement expander (expander) as a regenerator that converts gas pressure energy into power.
  • the expansion ratio of the positive displacement expander does not change. Reducing the rotational speed of the positive displacement expander and eliminating the pumping loss with respect to the decrease in the intake pressure means that the intake pressure of the positive displacement expander, that is, the regenerative pressure does not change. If the exhaust pressure of the positive displacement engine is kept constant even in a partial state, the exhaust pressure becomes too high with respect to the intake air that has been throttled and reduced by a throttle or the like, and problems such as abnormal combustion and backfire occur.
  • a variable valve mechanism is provided in the exhaust valve of a positive displacement expansion machine as a regenerator, and the opening timing of the exhaust valve is delayed as the intake pressure of the entire engine is lowered.
  • the intake valve timing of Miller cycle engines there are those with early closing and late closing, and when the intake pressure is reduced, the positive displacement expander reaches the same piston position on the expansion stroke side before the bottom dead center.
  • a method of advancing the opening timing of the exhaust valve is also included in the same inventive concept.
  • the opening timing of the exhaust valve of the positive displacement expander is delayed as the supercharging pressure is lowered.
  • the concept of the present invention is to control the opening timing of the exhaust valve of the positive displacement expander so that the regenerative pressure is appropriate for the positive displacement engine.
  • the appropriate regenerative pressure of a positive displacement engine is almost proportional to its intake pressure and output torque. Therefore, the concept of the present invention includes that the positive displacement engine is provided with an intake pressure sensor and an output torque sensor, and that the opening timing of the exhaust valve of the positive displacement expander is controlled according to the value.
  • the present invention also includes means for calculating the opening timing of the exhaust valve of the positive displacement expander from the map of the opening degree of the slot roll valve and the engine speed, thereby controlling the opening timing of the exhaust valve. Included in the concept.
  • regenerator and the positive displacement engine can be connected at a fixed ratio, the power transmission mechanism when the outputs of the positive displacement engine and the regenerator are combined into one is simplified.
  • the supercharger is most directly driven by the power from the regenerator. Is efficient. Further, a power transmission system from the positive displacement engine to the supercharger is not necessary. Further, by providing a variable mechanism in the intake valve of the positive displacement compressor, it is possible to control the output at the supercharging pressure. The throttle valve can be omitted, and the pumping loss of the positive displacement engine at the time of partial is reduced.
  • Cross section of positive displacement engine and positive displacement expander / compressor (Example 1) Enlarged view of the expansion machine exhaust valve and compressor intake valve (Example 1) Operation diagram of the expansion machine exhaust valve (Example 1) Explanatory drawing of opening and closing timing of compressor intake valve and expansion machine exhaust valve (Example 1) Explanatory drawing of opening and closing timing of compressor exhaust valve and expansion machine intake valve (Example 1) Explanation of interlocking mechanism of variable valve mechanism of compressor intake valve and expansion machine exhaust valve (Example 1) Cross-sectional view of swash plate type expander / compressor (Example 2) XX cross section of the expansion unit (Example 2) Deployment layout of the exhaust valve and exhaust port of the expansion machine and the intake valve and intake port of the compressor (Example 2) Skeleton diagram of power transmission system of positive displacement expander and positive displacement engine (Examples 3, 4, 5) Torque damper torque characteristics (Example 5) Cross section of single cylinder positive displacement engine and positive displacement expander / compressor (Example 6) YY
  • FIG. 1 is a cross-sectional view of one embodiment of the present invention.
  • 2 is a positive displacement engine (6-cycle engine), and 1 is a positive displacement expander as an exhaust regenerator.
  • the positive displacement expander 1 shares the positive displacement engine 2 and the crank pin 102.
  • the output shaft (crankshaft) 101 rotates clockwise.
  • the six-cycle engine 2 is a heat insulating engine, and a heat insulating cap 26 is provided on the upper surface of the piston 25.
  • the heat insulating cap 26, the upper portion of the inner wall 23 of the positive displacement engine cylinder, the combustion chamber 21, and the exhaust manifold 22 are on the surface. Is heat-insulated. A higher temperature gas can be sent into the positive displacement expander 1 by the heat insulation process.
  • the piston 110 of the positive displacement expander 1 is used for the expansion chamber 121 of the positive displacement expander as the regenerator on the upper surface and the compression chamber 321 of the positive displacement compressor 3 as the supercharger on the lower surface.
  • the piston 110 is provided with a head formed in a cup shape so as to cover the sliding portion side of the piston.
  • a gas seal portion 112 that partitions the expansion chamber 121 and the compression chamber 321 is provided on the outer periphery of the head.
  • the cylinder block 10 has a sliding surface 115 on which the piston slides and a gas sealing surface 111 on which the gas seal portion 112 slides, and these are formed by concentric cylindrical surfaces.
  • the piston 110 of this embodiment is formed with a central wall surface 113 for enhancing rigidity at the center in the output shaft direction, and the eccentricity of the head due to deformation of the piston is suppressed.
  • a histone pin 114 is engaged with the central wall surface 113, and the histone pin 114 is connected to the large end portion of the connecting rod 24 of the 6-cycle engine by two connecting rods 105 at both ends.
  • the volume of the expansion chamber 121 is originally required to be about twice the volume of the compression chamber 321.
  • the volume of the expansion chamber 121 is set to 1.2 times that of the compression chamber 321.
  • the aim is to reduce the size of the positive displacement expander as a regenerator.
  • there is no need to drive an extra capacity displacement type expander at the time of partial and there is an advantage that partial efficiency is improved.
  • the exhaust valve 140 of the expansion machine and the intake valve 330 of the compressor are provided on the opposite side of the positive displacement engine.
  • FIG. 2 is an enlarged view of the valves 140 and 330.
  • the valve drive shaft 161 is provided with eccentric cams 166 and 366 at a position of about 180 degrees, and rotates clockwise at the same rotational speed as the output shaft 101.
  • the valve drive mechanisms from the drive cams 166 and 366 are provided with the same mechanism vertically symmetrically.
  • the valves 140 and 330 swing linearly along the valve slide grooves 143 and 333 to open and close the exhaust port 142 of the expander and the intake port 332 of the compressor, respectively.
  • FIG. 3 is an explanatory diagram of the variable valve mechanism of the exhaust valve 140 of the expansion machine. Since the intake valve of the compressor has an upside down configuration, description thereof is omitted.
  • FIG. A shows the time when the exhaust valve 140 opens the exhaust port 142 to the maximum when the engine is idling.
  • the symbol of the member is FIG. See also C.
  • the pin 167 receives the rotational movement of the eccentric cam 166 via the valve drive connecting rod 165, and the rocker arm 168 swings around the rocker arm fulcrum shaft 172. Further, in conjunction with the rocking movement of the rocker arm 168, the exhaust valve 140 rocks up and down via the valve rod 173, the valve shifter 175, and the valve rod 174.
  • the two-dot chain line a is an arc centered on the end of the rod 173 on the valve shifter 175 side, and indicates the locus of the center of the rocker arm pin 169 that is the same as the valve opening amount in the figure.
  • the thin line b is a continuous trace of the center of the rocker arm pin 169 when the rocker arm is lifted to the maximum when the control shaft 171 is rotated. Since the line a and the line b are separated from each other, the control shaft 171 is connected to the FIG. A to FIG. It can be seen that the maximum opening of the valve increases as it rotates to an angle C. FIG. In A, a part of the rocker arm 168 is cut away so that the line a can be easily seen.
  • FIG. B shows the same idling state when the exhaust valve 140 is fully lifted to the closed side.
  • FIG. C when the engine is fully open and the exhaust valve 140 opens the exhaust port 142 to the maximum,
  • FIG. D indicates the time when the engine is fully opened and the exhaust valve 140 is lifted to the maximum side.
  • Rotating the control shaft 171 counterclockwise in this way increases the valve opening amount and the opening angle at the same time as increasing the valve timing. Since the intake valve of the compressor is configured to be turned upside down, rotating the control shaft 371 to the right slows the valve timing, and at the same time widens the valve opening and opening angle (see FIG. 2).
  • FIG. 4 shows the opening and closing timing of the intake valve of the positive displacement compressor as a supercharger by left rotation with the piston bottom dead center (BDC) as the upward (90 degrees) direction.
  • the four diagrams on the right side show the timing of the exhaust valve of the positive displacement expander as a regenerator by left rotation with the piston top dead center (TDC) as the upward direction.
  • VO represents the valve opening timing
  • VC represents the valve closing timing.
  • the figure on the first stage shows that the supercharging pressure when fully opened is 3 atm, the second stage is 1.8 atm, the third stage is 1 atm, the fourth stage is 0.5 atm used for engine idling, etc. The valve timing at this time is shown.
  • the closing timing of the compressor intake valve is advanced. By doing so, it is possible to reduce the intake air amount of the compressor and lower the supercharging pressure of the positive displacement engine. Since the function of the conventional throttle valve can be replaced by controlling the boost pressure, the pumping loss at the time of partial displacement of the positive displacement engine is reduced and the fuel consumption is improved.
  • the opening timing of the intake valve is after bottom dead center. Since the actual volume of the compression chamber 321 does not become zero at the bottom dead center of the piston, it is better not to open the valve until the internal gas expands to the intake pressure, so that the gas remaining in the compression chamber 321 flows back to the intake port. This is because the energy of the residual gas can be effectively utilized. Since this timing changes depending on the pressure, in this embodiment, the opening timing of the intake valve is advanced as the supercharging pressure is lowered.
  • the opening timing of the exhaust valve of the expansion machine is delayed as the boost pressure is lowered.
  • the negative pressure in the expansion chamber at the bottom dead center of the expansion machine becomes large, so that the exhaust is compressed after that and then exhausted.
  • the negative pressure of the gas inside the expansion chamber can be converted again into power, and the pumping loss is reduced.
  • the regenerative pressure is higher than the atmospheric pressure, the regenerative pressure is not equal unless the gas at atmospheric pressure is compressed. Therefore, when the exhaust valve is closed before top dead center, it is possible to suppress free expansion of the intake air in the expansion chamber when the intake valve is opened, and the regeneration efficiency is improved.
  • the exhaust valve of the expansion machine does not change the valve timing so much between the supercharging pressure of 3 atm and 1.8 atm. This is because the volume of the expansion chamber 121 is set in accordance with the supercharging pressure of 1.8 atm. It is also possible to use the same valve timing at 3 atm and 1.8 atm. In this embodiment, the opening timing is further advanced at 3 atmospheres because the expansion chamber pressure at the bottom dead center of the piston is already higher than the exhaust pressure and the frequency of use at high speed is high. Because I want to.
  • FIG. 5 is a diagram illustrating the exhaust valve timing of the compressor, and the diagram on the right side is an explanatory diagram of the intake valve timing of the expansion machine. These valves open and close at a constant timing regardless of the load.
  • FIG. 6 is an explanatory view of the interlocking mechanism of the variable valve mechanism of the intake valve of the compressor and the exhaust valve of the expansion machine.
  • FIG. The rotational positions of the A control shafts 171 and 371 indicate the fully opened position of the supercharging pressure of 3 atm.
  • Control pins 181 and 381 are driven into the respective control shafts 171 and 371, and the control pins 181 and 381 are engaged with the thrust cam 180. By moving the thrust cam 180 in the control axis direction, the control shafts 171 and 371 rotate.
  • FIG. 6 FIG. B is a developed view of the thrust cam 180 as viewed from the Z direction.
  • the dotted circle is the FIG.
  • the positions of the control pins 181 and 381 of A are shown on the development view.
  • the supercharging pressure is 3 atm.
  • the two-dot chain line indicates the position of the control pin whose supercharging pressure is 1.8 atm and 0.5 atm.
  • the intake valve control shaft 371 of the compressor rotates at a constant speed.
  • the exhaust valve control shaft 171 of the expansion machine rotates rapidly in the first half of the supercharging pressure from 0.5 atm to 1.8 atm, and does not rotate much after 1.8 atm.
  • FIG. 7 is a sectional view of the swash plate type expander / compressor 1 having six pistons 110.
  • the right side of the piston 110 is an expansion chamber 121 of the expansion machine, and the left side is a compression chamber 321 of the compressor.
  • the piston diameter on the expansion chamber side is larger and the volume ratio is 1.2.
  • the number of pistons in this embodiment is an even number of six because half of the compressor pistons are used for supercharging fresh air supplied to the intake ports of the six-cycle engine, and the other half are cooling supplied to the scavenging ports. This is because it is used for supercharging of the exhaust gas that has been exhausted.
  • the intake valve 130 of the expansion machine and the exhaust valve 340 of the compressor are directly attached to the output shaft 101 and are rotated to the right when viewed from the left.
  • the exhaust valve 140 of the expansion machine is integrated with the intake valve 330 of the compressor. It is formed in a cylindrical shape so as to enclose the expander / compressor as a whole, and is rotationally driven by a valve drive shaft 161 via valve drive gears 162 and 163.
  • the valve drive shaft 161 is driven from a sprocket 155 attached to the output shaft 101 via a chain 158 and a sprocket 156.
  • valve shifter 175. The positions of both side surfaces of the drive gear 163 formed integrally with the valve 140 are fixed by a valve shifter 175.
  • the valve 140 can be moved left and right through the valve shifter 175. In this figure, the valve 140 is on the far left and is at a supercharging pressure of 0.5 atm.
  • FIG. 8 is a cross-sectional view taken along the line XX in FIG. 7 and shows the relationship between the valve and the port of the positive displacement expander.
  • One intake port 132 and one exhaust port 142 are provided in each expansion chamber, whereas only one intake valve opening 131 is provided in the intake valve 130. Since the intake valve 130 rotates with the output shaft 101, the opening 131 is always at the same position with respect to the swash plate cam 151.
  • the exhaust valve 140 has five valve openings 141, and the valve 140 rotates to the left opposite to the output shaft 101 at a speed of 1/5.
  • the number of pistons is n
  • the number of valve openings 141 is (n ⁇ 1)
  • the rotational speed is 1 / (n ⁇ 1) of the rotational speed of the output shaft 101 (the rotational speed of the swash plate cam 151). It is.
  • FIG. 9 is a development arrangement view of the valve opening 141 and the exhaust port 142 of the exhaust valve 140 of the expansion machine of the present embodiment, and the valve opening 331 and the intake port 332 of the intake valve 330 of the compressor. Also in this embodiment, the supercharging pressure when fully opened is 3 atm, and the valve timing is substantially the same as in FIG. This figure is in a state of a supercharging pressure of 0.5 atm. As the valve rotates, the valve openings 141 and 331 move upward.
  • the two-dot chain line represents the position of the port having the widest opening angle when the supercharging pressure at which the valve 140 has moved to the right is 3 atm.
  • the shape of the port opening of the compressor and the shape of the port opening of the expansion machine are inclined in opposite directions. become.
  • the valve drive gears 162 and 163 use spur gears so that the opening shape is not inclined further.
  • the opening timing of the exhaust valve of the expansion machine is advanced when the intake pressure is lowered, both opening shapes are inclined in the same direction.
  • the shape of the opening can be shaped by using, as the valve drive gears 162 and 163, helical gears in the direction in which the rotation phase of the valve is delayed when the valve 140 is moved to the right.
  • FIG. A is a skeleton diagram of the power transmission system of the swash plate type expander / compressor 1 and the positive displacement engine 2 of the present embodiment.
  • the driving force from the positive displacement expander 1 is transmitted to the positive displacement engine 2 by the V-belt 411, and is output to the outside along with the driving force of the positive displacement engine 2 from one place on the flywheel 30 side.
  • FIG. B is a skeleton diagram of an embodiment using a power transmission system using the positive displacement expander 1 and the full can 421 of the positive displacement engine 2. Since displacement of a positive displacement engine is large, resonance is likely to occur in the drive system when connected to an expander having a rotary inertia mass via a highly rigid drive system. In the present embodiment, power transmission from the expansion machine 1 to the positive displacement engine 2 is performed through the full can 421, so there is no concern of resonance.
  • a one-way clutch 431 is provided in parallel with the full can 421, and transmits the driving force when the positive displacement engine 2 is started by the starter from the engine stopped state to the expander 1 without delay. This is because if the expansion machine 1 does not start to rotate quickly when the engine is started, a problem occurs in the positive displacement engine.
  • the output torque of the regenerator is larger than the driving torque of the turbocharger, it is necessary to consider the durability of the power transmission system. Since this embodiment uses the connecting chain 441, it is excellent in terms of durability.
  • the torque transmission capacity of the V-belt is determined by its tension, so it has the advantage of not transmitting more torque than necessary even if resonance occurs in the drive system, but has the disadvantage that the torque capacity is small, wear due to slip, and rubber deteriorates over time. There is.
  • FIG. C is a skeleton diagram of an embodiment in which a torsion damper 450 is used in a power transmission system in order to suppress drive system resonance. Since the connection chain 441 is used as in the third embodiment, it is excellent in terms of durability. Further, if the ratio is 1, unlike the second embodiment using a full can, there is an advantage that the displacement engine and the expansion machine can be arranged in a phase in which the primary inertia couple is canceled without changing the phase.
  • FIG. 11 is a characteristic diagram showing the torque characteristic of the torsion damper 450 in terms of a torsion angle.
  • the twist angle from the expander to the side that drives the positive displacement engine is positive.
  • the torsion damper 450 has a small spring rate at a positive torsion angle and a large torsion angle, whereas it hits the stopper at a small angle in the reverse direction, and the torsion angle is small.
  • the rigidity of the driving system is low due to the action of the torsion damper, the resonance frequency is lower than the engine speed, and no resonance occurs.
  • the torsion damper has a small twist angle and can transmit the driving force to the expander 1 without delay.
  • the torsion angle of the torsion damper is large in both directions, when the positive displacement engine 2 is started by the starter, the start-up of the expander 1 is delayed, a large displacement angle is given to the damper, and large elastic energy is stored. Therefore, when the expansion machine starts to rotate, the expansion machine and the positive displacement engine resonate due to the release of the elastic energy, and a mechanical sound is generated. In order to prevent this, the twist angle from the positive displacement engine to the side that drives the expander is reduced.
  • FIG. 12 is a cross-sectional view of a positive displacement expander / compressor 1 having a single cylinder positive displacement engine 2 and a crank pin 102 in common.
  • a 90 ° arrangement is adopted with respect to the positive displacement engine so that the primary inertia force can be canceled by the crankshaft 101 together with the weight of the reciprocating portion of the positive displacement engine.
  • the piston of this embodiment has sliding portions on both sides of the head having the seal portion 112.
  • the positive displacement engine 2 side is the expansion chamber 121, and the volume thereof is the same as the compression chamber 321 (volume ratio 1).
  • the expansion chamber 121 and the compression chamber 321 are formed of a cylinder gas seal surface component 520 and a compressor exhaust port component 530. At both ends there are sliding surface components 510, 540. These cylinder constituent members 510, 520, 530, and 540 are fixed to the crankcase 550 by the constituent members 510. The cylinder is arranged approximately horizontally in order to prevent the lubricating oil from falling from the sliding surface 115 to the expansion chamber 121 and the compression chamber 321 when the engine is stopped, and an oil drain 541 is formed in the component member 540.
  • the intake valve 130 of the expansion machine is formed in a desk shape and is arranged on the left side of the expansion chamber 121.
  • a cylindrical exhaust valve 140 of the expansion machine is integrated with a cylindrical intake valve 330 of the compressor and a desk-like exhaust valve 340 of the compressor.
  • valves 130 and 140 are rotated at a rotational speed that is 1/5 of the output shaft 101.
  • the exhaust valve 140 of the expansion machine is driven by a valve drive shaft 161 via drive gears 162 and 163.
  • the expansion valve intake valve 130 is engaged with the exhaust valve 140 with a claw and integrated.
  • the valve drive shaft 161 rotates on an axis orthogonal to the output shaft 101 from the output shaft 101 via the helical gears 562 and 563.
  • the portion below the two-dot chain line is shown as an external view in which the component member 510 and the case 550 are omitted.
  • the position of the valve does not move, and the port component 570 constituting the exhaust port 142 of the expander and the intake port 332 of the compressor can be moved to the left and right.
  • the port constituent member 570 and the cylinder constituent members 510 and 540 there are cylindrical flexible gas seals 512 and 542 for sealing the gas.
  • the exhaust port 142 of the expansion machine is connected to the exhaust pipe by flexible piping, and the port constituent member 570 is supported by a member that moves left and right so as not to rotate.
  • FIG. 13 is a cross-sectional view taken along the line YY in FIG. 12 and shows the relationship between the valves and ports of the positive displacement compressor.
  • the shapes of the intake valve opening 331 and the intake port 332 are the same as in FIG. 9, but the number of both is 5 for one cylinder.
  • the shape of the intake port 332 inside the valve 330 is wide in the circumferential direction, and is not involved in the opening / closing timing of the valve.
  • the five valve openings 331 and 341 of each valve simultaneously open and close the corresponding five ports 332 and 342. The same applies to the valves 130 and 140 on the compressor side.
  • valve rotation speed is 1 / n of the output shaft 101.
  • the valve opening cannot be omitted, but a part of the port can be omitted for convenience of arrangement.
  • the present invention provides a positive displacement engine with a regenerator that is less likely to reduce efficiency even in a partial state.
  • the positive displacement engine with a regenerator according to the present invention improves the efficiency at the time of partial, and is therefore highly likely to be used as an engine with a high frequency of partial use, such as an engine for a moving body.
  • a transmission or the like is not required for power transmission from the regenerator to the positive displacement engine, and the power transmission system is simplified.
  • a positive displacement expander / compressor that integrates a positive displacement compressor with a continuously variable valve mechanism in the intake valve is used as a regenerator / supercharger, the throttle valve can be omitted. The pumping loss at the time can be reduced. Further, by linking the control system of the continuously variable valve mechanism of the exhaust valve of the positive displacement expander and the intake valve of the positive displacement compressor, continuous and efficient output control can be performed by a single operation.
  • the six-cycle engine can easily use the positive displacement expander as a regenerator because of the feature that the exhaust gas temperature becomes lower due to the scavenging of exhaust gas. Further, an internal combustion engine equipped with a regenerator improves both output and efficiency as the boost pressure is increased. Therefore, the 6-cycle engine according to the present invention provided with a positive displacement expander / compressor as a regenerator / supercharger is highly feasible and has a great effect on improving the partial fuel consumption. Probability is high.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne une soupape d'échappement d'un détendeur volumétrique (un détendeur) comme régénérateur équipée d'un mécanisme à programme variable, et le moment d'ouverture de la soupape d'échappement est prévu pour être le dernier lorsque la pression d'admission de l'ensemble du moteur est prévue pour être la plus basse. Dans un état partiel, le gaz est expansé excessivement une seule fois dans une chambre d'expansion puis à nouveau comprimé, et la soupape d'échappement est ouverte au moment où la pression intérieure dans la chambre d'expansion devient supérieure à la pression atmosphérique, ce qui réduit la perte de pompage du détendeur volumétrique. Le moteur volumétrique présentant le régénérateur est si hautement efficace au moment partiel qu'une boîte de vitesses ou similaire n'est pas nécessaire pour la transmission de puissance du régénérateur au moteur volumétrique. Le détendeur volumétrique fait partie intégrante d'un compresseur volumétrique présentant le mécanisme de programme à variation continue dans une soupape d'admission, comme compresseur volumétrique, de sorte que le rendement-moteur peut être commandé par la commande de la pression de suralimentation, ce qui réduit la perte de pompage du moteur volumétrique par un papillon. Du point de vue de l'amélioration du kilométrage, par conséquent, le moteur volumétrique peut être particulièrement appliqué au moteur de machines motrices présentant des fréquences élevées de l'état partiel.
PCT/JP2009/058698 2009-05-08 2009-05-08 Moteur présentant un détendeur volumétrique comme régénérateur WO2010128558A1 (fr)

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PCT/JP2009/058698 WO2010128558A1 (fr) 2009-05-08 2009-05-08 Moteur présentant un détendeur volumétrique comme régénérateur
PCT/JP2009/065202 WO2010128567A1 (fr) 2009-05-08 2009-08-31 Compresseur à déplacement variable et expanseur à pression variable

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PCT/JP2009/065202 WO2010128567A1 (fr) 2009-05-08 2009-08-31 Compresseur à déplacement variable et expanseur à pression variable

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US20130340730A1 (en) * 2011-03-30 2013-12-26 Bayerische Motoren Werke Aktiengesellschaft Method for Operating a Volume-Controlled Internal-Combustion Engine, and an Internal-Combustion Engine

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JPS489108U (fr) * 1971-06-14 1973-02-01
JPS63215828A (ja) * 1987-03-03 1988-09-08 Mazda Motor Corp エンジンの過給装置
JPS63285222A (ja) * 1987-05-19 1988-11-22 Mazda Motor Corp エンジンの過給装置
JPH03242427A (ja) * 1990-02-16 1991-10-29 Ryokichi Tsuchiya ２サイクルエンジンにおける過給装置
JPH0417117U (fr) * 1990-05-31 1992-02-13

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130340730A1 (en) * 2011-03-30 2013-12-26 Bayerische Motoren Werke Aktiengesellschaft Method for Operating a Volume-Controlled Internal-Combustion Engine, and an Internal-Combustion Engine
US9435295B2 (en) * 2011-03-30 2016-09-06 Bayerische Motoren Werke Aktiengesellchaft Method for operating a volume-controlled internal-combustion engine, and an internal-combustion engine

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