EP3207234A1 - Dispositif de compensation des jeux de fonctionnement d'un moteur - Google Patents
Dispositif de compensation des jeux de fonctionnement d'un moteurInfo
- Publication number
- EP3207234A1 EP3207234A1 EP15753643.4A EP15753643A EP3207234A1 EP 3207234 A1 EP3207234 A1 EP 3207234A1 EP 15753643 A EP15753643 A EP 15753643A EP 3207234 A1 EP3207234 A1 EP 3207234A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- engine
- compensation device
- chamber
- transmission device
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 67
- 238000003825 pressing Methods 0.000 claims abstract description 39
- 239000012530 fluid Substances 0.000 claims description 30
- 238000006073 displacement reaction Methods 0.000 claims description 26
- 238000002485 combustion reaction Methods 0.000 claims description 10
- 238000005096 rolling process Methods 0.000 claims description 8
- 239000002775 capsule Substances 0.000 claims description 6
- 230000033001 locomotion Effects 0.000 abstract description 18
- 230000003068 static effect Effects 0.000 description 16
- 239000000203 mixture Substances 0.000 description 4
- 230000035939 shock Effects 0.000 description 3
- 230000006378 damage Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000010339 dilation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 230000009257 reactivity Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- 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
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
-
- 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
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
-
- 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
- F02B75/00—Other engines
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
Definitions
- the invention relates to a device for compensating the operating clearances of an engine, and in particular a variable volumetric ratio engine.
- An engine transmission device comprises a set of moving components providing or coming into play when transmitting the translational movement of a combustion piston in a cylinder to a rotational movement of a crankshaft.
- a transmission device capable of moving transversely, that is to say in a direction perpendicular to the axis of translation of the combustion piston, in an engine block. This displacement has its origin in the operating clearances existing between the mobile components of the transmission device. These operating clearances are notably affected by the manufacturing and assembly tolerances of the moving components, their wear, their deformation under load, and by the differential expansion of the parts of the engine subjected to different temperatures or formed of materials having different dilation.
- the operating games must be perfectly controlled. Too large, they lead to excessive acoustic emission of the engine during its operation, accelerated degradation of its components, or even its destruction for example by de-gearing components mobile. Too small, zero or negative, they lead to excessive friction between the moving components and therefore to a degraded engine performance, its blockage or even its destruction.
- static effort is meant a constant effort during a motor cycle.
- the static force is calibrated to oppose the maximum forces that apply to the transmission device, especially for the engine operating conditions (regime, load) causing the greatest effort.
- the static force ensures the permanent contact of the moving components of this device. It is therefore relatively important.
- the need for calibration of the holding force is particularly marked for a variable volumetric ratio motor, as described in the cited documents of the state of the art, and according to which a static holding force is applied to a side of a control rack whose longitudinal movement ensures the control of the volumetric ratio. Indeed, it is particularly important in this case to limit the static value of the holding force so as not to block or limit the movement of the control rack, in particular by sliding against the wall of the engine block.
- An object of the invention is to provide a device for compensating the operating clearances of a motor obviating the aforementioned drawbacks.
- the object of the invention proposes a device for compensating the operating clearances of an engine comprising:
- a transmission device capable of moving transversely in an engine block during an engine cycle
- the compensation device is remarkable in that the holding force is adjusted to the instantaneous speed of transverse displacement of the transmission device in the engine block.
- the compensation device allows the slow movements of the transmission device by applying a moderate holding force during these movements. It is opposed to the rapid movement of the transmission device, corresponding mainly to the peak of effort related to the combustion of the mixture in the cylinder, by applying a high holding force during these movements.
- the transmission device comprises:
- a control rack cooperating with a second side of the toothed wheel, and adapted to move longitudinally on an opposite wall of the engine block;
- the pressure device is integral with the engine block.
- the pressing device exerts the holding pressure on the control rack.
- the holding force has a threshold value
- the pressing device comprises a spring.
- the pressing device comprises:
- a piston operating in a chamber filled with a fluid and having at least one calibrated leakage orifice
- a source of pressure connected to the chamber
- the calibrated leak orifice is fluidly connected to the pressure source.
- the chamber, the cylinder and the check valve are integrated in a self-contained capsule.
- the pressure device is fluidly connected to a hydraulic unit.
- Figure 1 shows a schematic overall section of a particular configuration of the compensation device
- FIG. 2 shows a sectional view of a particular configuration of the pressing device
- FIG. 3 is a graphical representation of the evolution of certain parameters during an engine cycle of a variable volumetric ratio engine according to the state of the art.
- FIG. 4 is a graphical representation of the evolution of certain parameters during a motor cycle of a variable volumetric ratio motor according to the invention.
- FIG. 1 shows an overall and schematic cross-section of the device for compensating the functional clearances of an engine according to the invention and implemented in the case of a variable compression ratio engine.
- a motor unit 100 comprises at least one cylinder 110 in which a combustion piston 2 is displaced in translation, causing a crankshaft 9 to rotate by means of a transmission device 1.
- the transmission device 1 comprises a transmission member 3 secured to the combustion piston 2 and cooperating on the one hand with a rolling guide device 4 resting on a wall of the engine block 100 and on the other hand with a first side d a toothed wheel 5.
- the transmission member 3 is provided on one of its faces with a first rack of large dimension whose teeth cooperate with that of the toothed wheel 5.
- the transmission member 3 is also provided, in contrast to this first rack, another rack whose teeth of small dimensions cooperate with those of the roller 40 of the rolling guide device 4, integral with the engine block 100.
- the toothed wheel 5 cooperates with a connecting rod 6 connected to the crankshaft 9 in order to carry out the transmission of the movement.
- the toothed wheel 5 cooperates, on a second side opposite the transmission member 3, with a control rack 7 adapted to move longitudinally along an opposite wall of the engine block 100 and driven by a device control unit 12 comprising a control cylinder, whose piston cylinder is guided in a cylinder cylinder 112 of the engine block 100.
- the control rack 7 has teeth that cooperate with those of the toothed wheel 5 and may have a raceway which cooperates with a raceway of the toothed wheel 5.
- the control rack 7 also has on its opposite side a surface support 76 on which is exerted, in the particular configuration represented in FIG. 1, the force of maintaining a pressure device 10 integral with the engine block 100.
- the pressing device (10) is configured to adjust the holding force at the instantaneous transverse displacement speed of the transmission device (1) in the engine block (100).
- the control rack 7 and the control device 12 cooperate with the pressing device 10 so as to allow at least a vertical directional translation of the control rack.
- the pressing device 10 is integral with the engine block 100 and exerts the holding pressure on the transmission device 1 whose main components have just been listed. .
- the pressing device 10 can be incorporated in the transmission device 1, for example in the control rack 7 or the rolling guide device 4, and exert a force on one of the walls. of the engine block 100.
- the holding force is adjustable at the instantaneous speed of transverse displacement of the transmission device 1 in the engine block 100.
- various phenomena induce transverse displacements of the transmission device 1 according to two modes: a first mode of slow displacement, related to the gaps existing between the geometries or the real position of the parts and their ideal geometry, these deviations being able to be linked to deformation under effort, to manufacturing tolerances, differential expansion phenomena and wear. These movements have a period equal to a revolution of the crankshaft 9.
- a second mode of rapid movement resulting mainly from the peak force corresponding to the combustion of the mixture in the cylinder, and also resulting from the inertia of the movable members of the transmission device 1 in motion.
- the invention thus makes it possible to tolerate the slow displacements of the first mode which are necessary for the proper functioning of the engine; and effectively counteract the rapid movements of the second mode that could go against the proper functioning of the engine or degrade performance.
- the holding force is therefore not static as is the case in known solutions of the state of the art. Nor does it specifically depend on the position of the transmission device 1 in the engine block 100.
- the slow mode of displacement is preponderant, so that the average force applied to the transmission device during a motor cycle is relatively small; and much less important than that applied in the solutions of the state of the art.
- the average friction forces between the moving components are reduced, the motor efficiency is improved, and the dimensioning of the components of the transmission device 1, the motor unit 100, and the hydraulic power source can be reduced.
- An adjusted holding force means that the force exerted is variable according to the amplitude and / or direction of the instantaneous speed of the transmission device 1.
- the holding force will have a first value.
- the holding force In the absence of displacement or for instantaneous speeds of low displacement, the holding force will present a second value, less than the first.
- the second value is greater than a threshold force value, non-zero, that in all circumstances the pressing device exerts on the transmission device 1.
- the threshold value of the holding force ensures the cohesion and the cooperation of the mobile components of the transmission device 1 and its support on the opposite wall of the engine block 100 in the absence of peak effort exerted on the transmission device 1.
- cohesion and cooperation is meant that the moving components of the transmission device 10 are in contact or have a controlled clearance that does not affect the operation of the engine.
- the holding force can evolve continuously and continuously with the instantaneous transverse speed of the transmission device 1. It can also evolve from increasing and discontinuous manner, for example by step, with this speed.
- the first value of the holding force is determined to ensure the cohesion and cooperation of the mobile components of the transmission device 1 during peaks of effort.
- This first value can be variable with the speed of displacement. It can also be adjusted according to the load or the operating speed of the engine.
- the pressing device 10 may consist of a chamber 21, for example cylindrical, engaged in an orifice arranged in the engine block 100.
- the pressing device 10 is assembled in the engine block by attachment means 22, comprising for example a flange secured to the device and bolts screwed into the engine block 100.
- the chamber 21 is provided with a piston 23, confining the fluid in the chamber 21, and able to evolve in translation in this chamber.
- the holding force is exerted on the transmission device 1 via the piston head 23.
- Sealing means are arranged between the cylinder and the piston 23.
- the piston 23 comprises a projecting central portion 24, releasing an annular space with the inner surface of the piston liner 23, for accommodating a spring 25, as will be discussed in detail later.
- the piston head 23 has an exposed surface 20 adapted to cooperate with a bearing surface 76 of the control rack 7.
- the chamber 21 is filled with a fluid such as oil, water or a gas. This may for example be the engine lubricating oil. Preferably, it is a hydraulic fluid.
- the chamber 21 is also provided with at least one calibrated leak orifice 28. This allows a flow of the fluid outside the chamber, in particular when a pressure is applied to the fluid via the piston.
- the chamber 21 is supplied with fluid by a pressure source such as an accumulator (not shown in FIG. 2) fluidly connected to the chamber 21, for example by supply means such as a conduit and / or a tuned channel in the chamber 21 and opening into a supply zone 31 of the chamber 21.
- a pressure source such as an accumulator (not shown in FIG. 2) fluidly connected to the chamber 21, for example by supply means such as a conduit and / or a tuned channel in the chamber 21 and opening into a supply zone 31 of the chamber 21.
- a check valve 32 arranged between the chamber and the source of pressure ensures the maintenance of a minimum permanent pressure of the fluid within the chamber, identical to the pressure present in the source, and interrupts any power supply when, under the effect of a force exerted on the piston 23, the pressure of the fluid in the chamber exceeds the pressure of the fluid in the source.
- the check valve 32 may comprise a ball 33 positioned in a bore of the chamber 21 and closing a supply channel from the feed zone 31 when the fluid pressure of the chamber 1 brings to the stop of the canal.
- the combined arrangement of the piston 23 evolving in a chamber 21 filled with a fluid and having at least one calibrated leakage orifice 28, the pressure source connected to the chamber 21 and the nonreturn valve 32 between the source and the chamber 21 results in a device adapted to provide a force adjusted to the speed of movement of the piston 23.
- the fluid contained in the chamber 21 flows through the calibrated leak orifice without generating significant overpressure in the chamber; and the piston 23 exerts a low resistance force substantially equivalent to its precharging threshold value.
- the fluid contained in the chamber can not flow sufficiently and rises in pressure, the piston 23 then exerts a high resistance force much greater than the precharging threshold value.
- the relationship linking the force to the speed can be calibrated by adjusting for example the dimension of the calibrated leakage orifice 28 of the chamber 21.
- the chamber 21 is also provided with a spring 25, for example helical as shown in Figure 2. It may also be a spring type "Belleville".
- the spring 25 may be disposed in the annular space formed between the central portion 24 and the inner surface of the piston liner 23, as shown in FIG. 2, but it may also be disposed outside the chamber.
- the pressure exerted by the hydraulic portion of the pressure device 10 complements the pressure exerted by the spring 25.
- This hydraulic portion may then have a smaller dimension and in particular have a reduced fluid static pressure.
- the spring 25 may be chosen so that it contributes between 20% and 40% to the level of threshold force exerted by the pressing device 10. Preferably, this contribution will be chosen at 33%.
- the presence of the spring 25 also ensures a better reactivity of the pressing device 10 during the oil replenishment phases during which the piston 23 must nevertheless quickly exert pressure on the control rack 7.
- the presence of the spring 25 allows the engine to operate in a degraded mode in case of failure of the hydraulic part of the pressing device 10 by guaranteeing the functionality of the pressing device 10 over a limited engine operating range.
- the pressing device 10 may comprise a calibrated leakage orifice 28 fluidly connected to the pressure source. This connection can be made by conduits if the pressure source is offset, or the calibrated leakage orifice 28 can directly supply a reservoir of this pressure source.
- the chamber 21, the piston 23 and the check valve 31 may advantageously be integrated in an independent capsule then forming an independent pressing device 10.
- the pressure source may be fluidically connected to all the pressure devices 10 of the engine in the context of a centralized hydraulic management.
- the calibrated leakage orifice 28 can be disposed in the piston 23 itself and open at the exposed surface 23, in particular to lubricate the surfaces. contact of the control rack 7 and the pressing device 10.
- a pump of the hydraulic unit can be provided for adjusting the static pressure of the fluid in the pressure source, and consequently the static pressure of the fluid in the pressing device 10. This adjustment can be determined according to the load and the operating speed. engine operation.
- the hydraulic unit may include a computer, connected to sensors to measure among others the load level and the speed. The computer determines a target static pressure and drives the pump to bring the static pressure of the accumulator to the target static pressure.
- the particular configuration of the pressing device 10 shown in Figure 2 has a single calibrated leakage orifice 28; but additional calibrated leak holes may have been provided.
- Figure 2bis shows another embodiment of a pressing device 10 for exerting a holding force according to the invention.
- the piston 23 the chamber
- the pressing device 10 is associated with a pressure source 33 consisting of a reservoir 34, comprising a sealed membrane confining the fluid in the reservoir 34 of the source.
- An opening 36 of the source makes it possible to introduce a gas, making it possible to pressurize the fluid contained in the tank 34.
- the calibrated leakage orifice is integrated with the check valve 37. It comprises a ball 38 positioned in a bore of the chamber communicating towards the source of pressure 33. A spring 39 is positioned in the bore, between the ball 38 and a wall of the pressure source.
- the spring retains the displacement of the ball and allows the flow of fluid to the source, thus forming the calibrated leakage orifice 29.
- the spring is compressed so that the ball completely closes the calibrated leakage orifice 29.
- the pressing device 10 can also form a mechanical stop for the transmission device 1.
- This stop is exerted for example when the end of the piston liner 23 or the central portion 24 of it comes into contact with the bottom of the chamber 21.
- This mechanical stop is however not intended to be solicited in normal operation of the engine, but may be a safety means to prevent disengagement of the mobile components of the device transmission 1 in case of anomalies such as a failure of the hydraulic system of the engine, and in addition to the spring when it is present.
- FIG. 3 is a graphical representation of the evolution of certain parameters of a 4-stroke engine with a variable volumetric ratio during an engine cycle. ie during a 720 ° rotation of the crankshaft.
- the engine is equipped with a hydraulic cylinder exerting a static force on the transmission device of this engine.
- Figure 3a shows the evolution of the pressure in the cylinder. There is a steep peak of pressure corresponding to the explosion of the combustion mixture in the cylinder.
- Figure 3b shows the displacement of the transmission device during the engine cycle; and
- Figure 3c shows the speed of the transmission device during the engine cycle.
- These figures show the slow mode of movement, exhibiting displacements of small amplitudes (of the order of 0.1 mm) and of low speed during most of the engine cycle.
- Figure 3d shows the pressure applied by the hydraulic cylinder on the transmission device. It is noted that it has a static level of about 6kN.
- FIG. 4 is a graphical representation of the evolution of the parameters of a variable volumetric ratio engine, comprising the pressing device 10 of the invention, thus exerting a holding force adjusted to the instantaneous transverse displacement speed of the transmission device. .
- the pressing device 10 is made by an independent capsule, comprising a piston operating in a chamber filled with a fluid and having at least one calibrated leak orifice, an external pressure source of 30 bars. is connected to the chamber, and a non-return valve disposed between the source and the chamber.
- FIG. 4a represents the evolution of the pressure in the cylinder, similar to what has been represented in FIG. 3a in the solution of the state of the art.
- Figures 4b and 4c respectively show the displacement and the speed of the transmission device 10 during the engine cycle.
- the slow displacement mode has displacements of amplitudes similar to those shown in FIG. 3b, of the order of 0.1 mm.
- pressing device 10 for the purposes of the complete description of the invention, it may in certain cases be preferred, without departing from the scope of the invention, to use other forms of pressing device performing the same functions as those described. It may thus be for example a device comprising shock absorption means based on viscous or highly viscous polymer as disclosed in US5495923; or comprising electromagnetic shock absorbing means as disclosed in US7537097
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1459791A FR3027051B1 (fr) | 2014-10-13 | 2014-10-13 | Dispositif de compensation des jeux de fonctionnement d'un moteur. |
PCT/EP2015/068105 WO2016058724A1 (fr) | 2014-10-13 | 2015-08-05 | Dispositif de compensation des jeux de fonctionnement d'un moteur |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3207234A1 true EP3207234A1 (fr) | 2017-08-23 |
EP3207234B1 EP3207234B1 (fr) | 2019-01-16 |
Family
ID=52450317
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15753643.4A Active EP3207234B1 (fr) | 2014-10-13 | 2015-08-05 | Dispositif de compensation des jeux de fonctionnement d'un moteur |
Country Status (8)
Country | Link |
---|---|
US (1) | US10202899B2 (fr) |
EP (1) | EP3207234B1 (fr) |
JP (1) | JP6603316B2 (fr) |
KR (1) | KR102076039B1 (fr) |
CN (1) | CN107110015B (fr) |
ES (1) | ES2718933T3 (fr) |
FR (1) | FR3027051B1 (fr) |
WO (1) | WO2016058724A1 (fr) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3029977B1 (fr) | 2014-12-12 | 2018-11-30 | MCE 5 Development | Dispositif de transmission d'un moteur, notamment pour un moteur a taux de compression et/ou a cylindree variable. |
FR3051838B1 (fr) | 2016-05-24 | 2018-09-07 | MCE 5 Development | Dispositif de guidage a roulement d'un piston de combustion pour un moteur a taux de compression variable |
FR3063307B1 (fr) * | 2017-02-28 | 2019-03-29 | MCE 5 Development | Dispositif presseur pour exercer un effort de maintien sur un dispositif de transmission et moteur muni d’un tel dispositif. |
FR3081929B1 (fr) * | 2018-06-04 | 2020-09-18 | MCE 5 Development | Dispositif de chemise pour verin de commande d’un moteur a combustion interne |
US11187184B2 (en) * | 2019-03-29 | 2021-11-30 | Vianney Rabhi | Articulated plenum for transfer-expansion-regeneration combustion engine |
CN110594017A (zh) * | 2019-09-05 | 2019-12-20 | 辽宁工程技术大学 | 一种汽车发动机可变压缩比机构 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4433649A (en) * | 1981-11-27 | 1984-02-28 | Shin Hi B | Engine |
JPS60185003U (ja) * | 1984-05-18 | 1985-12-07 | マツダ株式会社 | ゼロラツシユ調整装置 |
JPH06137226A (ja) * | 1992-10-28 | 1994-05-17 | Toyoda Gosei Co Ltd | 燃料遮断装置 |
PL170036B1 (pl) | 1993-04-28 | 1996-10-31 | Urzadzen Mechanicznych Kamax S | Amortyzator elastomerowy PL |
US5674053A (en) * | 1994-04-01 | 1997-10-07 | Paul; Marius A. | High pressure compressor with controlled cooling during the compression phase |
JPH09209787A (ja) * | 1996-02-02 | 1997-08-12 | Nissan Motor Co Ltd | 圧縮比可変式直噴ディーゼルエンジン |
CN100398868C (zh) | 2003-07-31 | 2008-07-02 | 财团法人生产技术研究奖励会 | 电磁阻尼器控制装置 |
FR2867515B1 (fr) * | 2004-03-11 | 2006-06-02 | Vianney Rabhi | Dispositif de reglage pour moteur a rapport volumetrique variable |
FR2896539B1 (fr) * | 2006-01-26 | 2008-05-02 | Vianney Rabhi | Dispositif presseur pour moteur a rapport volumetrique variable. |
FR2896535B1 (fr) * | 2006-01-26 | 2008-05-02 | Vianney Rabhi | Dispositif de refroidissement et de lubrification par projection d'huile pour moteur a rapport volumetrique variable |
FR2919022B1 (fr) * | 2007-07-19 | 2012-10-26 | Vianney Rabhi | Centrale hydraulique pour moteur a taux de compression variable. |
CN103541819B (zh) * | 2012-07-17 | 2017-08-08 | 瓦锡兰瑞士公司 | 大型往复活塞式燃烧发动机及其控制设备和控制方法 |
KR101338461B1 (ko) * | 2012-11-02 | 2013-12-10 | 현대자동차주식회사 | 가변 압축비 장치 |
KR101382318B1 (ko) * | 2012-12-17 | 2014-04-10 | 기아자동차 주식회사 | 가변 압축비 장치 및 이를 이용한 내연기관 |
-
2014
- 2014-10-13 FR FR1459791A patent/FR3027051B1/fr not_active Expired - Fee Related
-
2015
- 2015-08-05 KR KR1020177012144A patent/KR102076039B1/ko active IP Right Grant
- 2015-08-05 WO PCT/EP2015/068105 patent/WO2016058724A1/fr active Application Filing
- 2015-08-05 ES ES15753643T patent/ES2718933T3/es active Active
- 2015-08-05 US US15/518,977 patent/US10202899B2/en active Active
- 2015-08-05 CN CN201580067380.3A patent/CN107110015B/zh active Active
- 2015-08-05 EP EP15753643.4A patent/EP3207234B1/fr active Active
- 2015-08-05 JP JP2017520969A patent/JP6603316B2/ja active Active
Also Published As
Publication number | Publication date |
---|---|
WO2016058724A1 (fr) | 2016-04-21 |
ES2718933T3 (es) | 2019-07-05 |
KR20170085040A (ko) | 2017-07-21 |
US20170234215A1 (en) | 2017-08-17 |
JP2017531759A (ja) | 2017-10-26 |
FR3027051A1 (fr) | 2016-04-15 |
CN107110015B (zh) | 2020-01-10 |
CN107110015A (zh) | 2017-08-29 |
KR102076039B1 (ko) | 2020-02-11 |
EP3207234B1 (fr) | 2019-01-16 |
JP6603316B2 (ja) | 2019-11-06 |
FR3027051B1 (fr) | 2016-11-25 |
US10202899B2 (en) | 2019-02-12 |
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