EP1740810B1 - Dispositif de reglage pour moteur a rapport volumetrique variable - Google Patents

Dispositif de reglage pour moteur a rapport volumetrique variable Download PDF

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Publication number
EP1740810B1
EP1740810B1 EP05736556A EP05736556A EP1740810B1 EP 1740810 B1 EP1740810 B1 EP 1740810B1 EP 05736556 A EP05736556 A EP 05736556A EP 05736556 A EP05736556 A EP 05736556A EP 1740810 B1 EP1740810 B1 EP 1740810B1
Authority
EP
European Patent Office
Prior art keywords
adjustment device
engine block
thruster
piston
cylinder
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.)
Not-in-force
Application number
EP05736556A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1740810A1 (fr
Inventor
Vianney Rabhi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
RABHI, VIANNEY
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Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1740810A1 publication Critical patent/EP1740810A1/fr
Application granted granted Critical
Publication of EP1740810B1 publication Critical patent/EP1740810B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
    • 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
    • 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

Definitions

  • the present invention relates to an adjustment device integrated in an engine block for adjusting the functional clearances, and the positioning of a transmission device of a variable volumetric ratio engine while giving it the angular freedom necessary for its operation. .
  • the change in the effective displacement of the engine is effected by discharging into the intake manifold excess fresh gases allowed in the cylinder and by controlling the stroke length used to compress the gases by means of a valve. additional admission with delay variable closure.
  • the adjustment of the effective volumetric ratio of the engine is effected by modifying the original position of the stroke of a piston relative to a cylinder, by means of a toothed wheel mounted free at the upper end of a cylinder. connecting rod, a transmission member secured to the piston and a control rack whose position is adjusted by a control device.
  • the mechanical transmission device for a variable displacement motor comprises a piston integral in its lower part with a transmission member cooperating on the one hand with a rolling guide device and on the other hand with a gear wheel secured to a connecting rod for transmitting the movement between said piston and said connecting rod.
  • the mechanical transmission device for a variable displacement motor comprises at least one cylinder in which a piston moves which is secured, in its lower part, with a transmission member cooperating on the one hand by means of a small rack with a rolling guide device, and secondly by means of another rack of large dimension with a toothed wheel secured to a connecting rod, a control rack cooperating with the gear wheel, means of fixing the piston on the transmission member which provide a clamping preload, connecting means which make it possible to stiffen the teeth of the racks, and means for reinforcing and lightening the structure of the toothed wheel.
  • the adjustment device aims to adjust the functional clearances, and the positioning of a transmission device of a variable compression ratio engine while giving it the angular freedom required for its operation, the set being integrated in an engine block.
  • the adjustment device comprises, at the level of the rolling guide device, means for adjusting the positioning of the transmission device, and at the level of the control rack means for adjusting the functional clearances of the transmission device.
  • the adjusting device comprises a control device comprising, at the level of the jack piston of a control cylinder, first means giving the transmission device the angular freedom required for its operation.
  • the adjusting device comprises a control rack having second means giving to the transmission device the angular freedom necessary for its operation and acting more particularly between said control rack and the engine block.
  • the adjusting device comprises at the level of the rolling guide device positioning adjustment means which consist of an orifice pierced in the engine block on the side of the cylinder and which makes it possible to introduce into said block a support having racks for synchronizing the movement of a roller with that of the piston, and a rolling track cooperating with said roller.
  • the adjustment device comprises a support which consists of a thick plate which allows its attachment to the engine block, by the outside of the latter, by means of screws.
  • the adjusting device comprises a body which is attached to the support, said body having rolling tracks, and being fixed to said support with at least one fixing screw.
  • the adjusting device according to the present invention comprises a seal between the support and the engine block which is provided by a seal housed in a groove in the support.
  • the adjusting device according to the present invention comprises a seal between the support and the engine block which is provided by a seal housed in a groove in the engine block.
  • the adjusting device comprises adjusting means consisting of a shim interposed between the inner face of the thick plate and the outer face of the engine block.
  • the adjustment device comprises, at the level of the control rack, means for adjusting the functional clearances which consist of a bearing face whose distance relative to the engine block is adjustable.
  • the adjusting device according to the present invention comprises a flat face which is formed on a cylindrical support screwed into the engine block.
  • the adjusting device according to the present invention comprises a cylindrical support which has a threading made around its circumference to be screwed directly into a threaded hole arranged in the engine block.
  • the adjusting device comprises a cylindrical support which comprises a tool socket allowing its clamping and its holding in position during its locking by means of a counter nut.
  • the adjusting device comprises a counter nut which comprises a tool socket allowing its tightening, provided so that one can tighten the nut while maintaining the cylindrical support by means of its tool socket .
  • the adjusting device comprises a cylindrical support which is secured to a thick plate, fixed from the outside to the engine block by means of screws and whose distance from the engine block is regulated by a shim placed between the thick plate and the engine block.
  • the adjusting device comprises a control cylinder of the control device which consists of an upper cylinder rod having a threaded portion allowing its attachment with the lower cylinder rod of the control rack and a piston a cylinder traversed in its center, by means of a bore, by the upper cylinder rod, said upper cylinder rod having centering means for centering on the one hand the upper cylinder rod on the cylinder piston and on the other hand the lower cylinder rod on the cylinder piston.
  • the adjusting device comprises a cylinder piston whose part in contact with a cylinder cylinder has a spherical profile forming a ball-type connection between said piston cylinder and said cylinder cylinder.
  • the adjusting device according to the present invention comprises a cylinder piston which comprises on either side of its spherical profile of the ethane gaskets.
  • the adjusting device according to the present invention comprises a jack piston which includes a discharge valve.
  • the adjusting device comprises a cylinder piston which comprises a discharge valve consisting of a ball held on a seat formed in said piston cylinder by a spring.
  • the adjusting device comprises a control rack which comprises, opposite its teeth, a bearing face comprising a cavity in a portion of a sphere which is provided to receive a cap in sphere portion of a support piece housed in said cavity and providing a ball joint connection between the control rack and the engine block.
  • the adjustment device comprises a control rack whose cavity has at its pole a housing, while the cap has at its pole another housing, said housing allowing the establishment of a spring.
  • the adjusting device comprises a jack piston which is traversed vertically by a bore for the passage of a control rod cooperating on either side of the thickness of the jack piston with valves and springs. .
  • the adjustment device comprises valves which are each traversed by the control rod and which bear directly on the corresponding upper or lower face of the piston cylinder.
  • the adjustment device comprises springs which are each traversed by the control rod and which bear on the one hand on the corresponding valve and on the other hand on a stop provided on the control rod.
  • the adjusting device according to the present invention comprises valves each having a seal which is composed of a friction-resistant plastic ring and an internal O-ring sealing between the ring and the valve body. .
  • the control device comprises valves each having a small contact surface with the cylinder piston, embodied by a peripheral circular edge provided to increase the contact pressure exerted by said valves on said cylinder piston.
  • the adjusting device comprises a cylinder cylinder which is directly bored in the engine block and closed in its upper part by a cylinder head which is screwed on the engine block.
  • FIG. 1 to 3 We have shown in Figures 1 to 3 an engine block 100 which comprises at least one cylinder 110 in which a piston 2 moves by means of a transmission device 1.
  • the mechanical transmission device 1 comprises in the lower part of the piston 2 a transmission member 3 secured to said piston and cooperating, on the one hand with a rolling guide device 4, and on the other hand with a toothed wheel 5.
  • the toothed wheel 5 cooperates with a connecting rod 6 connected to a crankshaft 9 in order to carry out the transmission of the movement between said piston and said crankshaft.
  • the toothed wheel 5 cooperates opposite the transmission member 3 with another rack called control rack 7 whose vertical position relative to the engine block 100 is controlled by a control device 12 comprising a control cylinder 8, whose piston cylinder 13 is guided in a cylinder cylinder 112 arranged in the engine block 100.
  • the cylinder cylinder 112 can be directly bored in the engine block 100, or in a not shown sleeve reported in the engine block 100.
  • the cylinder cylinder 112 is closed in its upper part by a cylinder head 113 which is screwed on the Engine block 100.
  • the transmission device 1 comprises a transmission member 3 secured to the piston 2 and provided on one of its faces with a first large-sized rack 35 whose teeth 34 cooperate with those 51 of the toothed wheel 5.
  • the transmission member 3 comprises, opposite the rack 35, another rack 37 whose teeth 38 of small dimension cooperate with those of the roller 40 of the rolling guide device 4 integral with the engine block.
  • the engine block 100 is pierced with a hole 104 on the side of the cylinder 110 for introducing into said block a support 41 having racks 46 ensuring the synchronization of the movement of the roller 40 with that of the piston 2, and a raceway 48 cooperating with the roller 40.
  • the support 41 consists of a thick plate 42 which allows it to be fastened to the engine block 100 from the outside of the latter by means of screws 105.
  • a body 45 having the raceway 48 cooperating with the roller 40 can be reported on said support 41 a body 45 having the raceway 48 cooperating with the roller 40, said body being fixed to said support 41 with at least one fixing screw 107 .
  • the seal between the support 41 and the engine block 100 is provided by a seal 47 housed in a groove 44 which may be formed either in the support 41 or in the engine block 100.
  • the distance between the engine block 100 and the support 41 is adjusted by a shim 106, forming means for adjusting the positioning of the transmission device 1, said shim 106 being interposed between the inner face of the plate 42 and the face external motor block 100.
  • the shim 106 makes it possible to adjust the control rack 7 in the vertical position, taking into account the stacking of the ribs of all the parts comprised between the bearing plane of the support 41 on the engine block 100 and the center of the cylinder cylinder 112 of the control cylinder 8.
  • the thickness of the shim 106 is determined after measuring the stacking of the ribs of all the parts comprised between the bearing plane of the support 41 on the engine block 100 and the center of the cylinder cylinder 112 of the control cylinder 8.
  • control jack 8 of the control device 12 which consists of an upper cylinder rod 10 having a threaded portion 11 screwed into the lower cylinder rod 16 of the control rack 7 and a piston of cylinder 13 traversed in the middle, by means of a bore 17, by the upper cylinder rod 10.
  • the upper cylinder rod 10 has a cylindrical portion 14 cooperating with a bore 114 formed in the cylinder head 113 providing the actuating cylinder 8 a ratio between displaced volume and cylinder piston stroke 13 which is identical for the upper chambers 121 and lower 122.
  • the upper cylinder rod 10 has a tool socket 15 allowing it to be clamped.
  • the upper cylinder rod 10 comprises centering means 135 which make it possible to center on the one hand the upper cylinder rod 10 on the jack piston 13 and on the other hand the lower cylinder rod 16 on the jack piston 13.
  • the lower cylinder rod 16 may have a threaded portion screwed into the upper cylinder rod 10, and centering means that center on the one hand the upper cylinder rod 10 on the cylinder piston 13 and on the other hand the lower cylinder rod 16 on the cylinder piston 13.
  • the seal between the upper cylinder rod 10 and the bore 114 of the cylinder head 113 is provided by a seal 115.
  • the seal between the lower cylinder rod 16 and a bore 116 formed in the bottom 117 of the cylinder cylinder 112 is provided by a seal 118.
  • the seals 115 and 118 are provided to be able to seal while accommodating the large clearance provided between the upper and lower cylinder rods 16 and their respective bores 114, 116.
  • This arrangement allows the control rack 7 to orient in the motor block 100 so that the teeth 74 of said rack align with those 52 of the toothed wheel 5.
  • Each seal 115 and 118 is composed of, for example, an outer ring 119 of friction-resistant plastics material and an inner O-ring 120 which seals between the ring 119 and the corresponding bore 114, 116.
  • the cylinder piston 13 is traversed vertically by another bore 18, with or without at least one countersink 19 for limiting the overall size of the control device 12, for the passage of a control rod 20 cooperating on both sides of the thickness of the piston 13 with valves 21 and springs 22.
  • Each valve 21 is traversed by the control rod 20 and bears directly on the corresponding upper or lower face of the jack piston 13 or counterbore 19.
  • Each spring 22 is traversed by the control rod 20 and is supported on the one hand on the corresponding valve 21 and on the other hand on a stop 130 arranged on the control rod 20 and consisting, for example, of a ring elastic 131 and a washer 132.
  • Each valve 21 comprises a seal which is composed, for example, of a friction-resistant plastic ring 23 and an internal O-ring 24 which seals between the ring 23 and the body of the valve 21.
  • the valves 21 may be provided in two parts to facilitate the assembly of the seal they comprise.
  • valves 21 and the control rod 20 are sufficient to allow the jack piston 13 to pivot slightly in the cylinder cylinder 112 so that the control rack 7 can be oriented in the engine block 100 so that the teeth 74 of said rack are aligned with those 52 of the toothed wheel 5, while allowing said valves to seal between the upper chamber 121 and lower 122 of the cylinder cylinder 112.
  • valves 21 can therefore pivot slightly relative to the control rod 20 so that they always remain in contact on their entire circumference with the piston cylinder 13.
  • Each valve 21 may have a small contact surface with the piston of cylinder 13, materialized by a circular peripheral edge 25 provided for increasing the contact pressure exerted by said valves 21 on said piston cylinder 13.
  • This arrangement makes it possible on the one hand to ensure a better seal and on the other hand to the valves 21 to provide a surface exposed to the pressure of the piston-type fluid on the larger cylinder 13 in order to facilitate the control of the control device 12.
  • the control rod 20 comprises, for its guidance, a cylindrical portion 123 cooperating with a bore 124 formed in the cylinder head 113.
  • the control rod 20 comprises in the extension of its cylindrical portion 123 a threaded end 125 for its attachment to a steering device not shown.
  • the seal between the control rod 20 and the bore 124 of the cylinder head 113 is provided by a seal 126.
  • the bore 124 may comprise a counterbore 133 in which the spring 22 and the stopper 130 located in the upper cylinder chamber 121 may be developed, in order to limit the vertical dimensions of the control device 12.
  • control rod 20 is guided in a bore 127 formed in the bottom 117 of the cylinder cylinder 11 2.
  • the seal between the control rod 20 and the bore 127 of the cylinder cylinder 112 is provided by a seal 128.
  • the bore 127 may comprise a counterbore 134 in which the spring 22 and the stop 130 located in the lower cylinder chamber 122 can be developed, in order to limit the vertical dimensions of the control device 12.
  • the portion of the jack piston 13 in contact with the cylinder cylinder 112 has a spherical profile 26 forming a ball-type connection between said jack piston 13 and said cylinder cylinder 112.
  • This arrangement is provided to allow the control rack 7 to pivot so that its teeth 74 can align with the teeth 52 of the toothed wheel 5.
  • the piston of cylinder 13 comprises on both sides of its spherical profile 26 seals 27.
  • the seals 27 are provided for sealing between the upper chamber 121 and the lower chamber 122 of the control jack 8, despite the large clearances required for the orientation of the jack piston 13 in the cylinder cylinder 112.
  • the seals 27 are composed, for example, of an outer ring made of friction-resistant plastic material and an internal O-ring which seals between the ring and the jack piston 13.
  • the spherical profile 26 of the jack piston 13 forms first means giving the angular freedoms necessary for the operation of the transmission device 1.
  • the piston of cylinder 13 may comprise a discharge valve 137 which may consist, for example, of a ball 138 held on a seat formed in the jack piston 13 by a spring 139 ( figure 10 ).
  • the relief valve 137 makes it possible to limit the maximum pressure of the upper chamber 121 of the control jack 8, and thus makes it possible to limit the maximum force exerted on the teeth 34, 51, 52, 74 of the transmission device 1 .
  • the control rack 7 comprises, opposite its teeth 74, a bearing face 75 that cooperates with a bearing face 103 formed in the motor block 100 and whose distance relative to said motor block 100 is adjustable, this constituting means for adjusting the functional clearances of the transmission device 1.
  • the bearing face 75 comprises a cavity 28 in the sphere portion having or not at its pole a cylindrical housing 29 for a spring 30 which may be, for example, helical type or "belleville".
  • the function of the spring 30 is to maintain in contact the various members of the transmission device 1, when a small force is exerted on the teeth 51, 52 of the toothed wheel 5.
  • the cavity 28 is designed to receive the cap 31 as a sphere portion of a bearing piece 76 housed in said cavity forming a ball joint connection between the control rack 7 and the engine block 100 ( figure 5 ).
  • the spherical portion cap 31 of the support piece 76 may have at its pole a cylindrical housing 36 for the spring 30.
  • the bearing piece 76 has, opposite its cap in the sphere portion 31, a plane face 32 cooperating with another plane face 103 formed in the motor block 100.
  • This arrangement allows the control rack 7 to move relative to the engine block 100.
  • the support piece 76 can comprise a network of channels 33 for bringing the lubricating oil on the one hand on its flat face 32 and on the other by its cap in sphere portion 31.
  • the ball-type connection between the control rack 7 and the engine block 100 formed by the spherical profile of the cavity 28 of said control rack 7 and by the spherical portion cap 31 of the support piece 76 constitutes second means giving the angular freedoms necessary for the operation of the transmission device 1.
  • the plane face 103 of the motor unit 100 is made, for example, on a cylindrical support 102 screwed into said block.
  • the cylindrical support 102 has a threading 108 made on its periphery to be screwed directly into a threaded hole 101 provided in the engine block 100.
  • the cylindrical support 102 comprises a tool socket 109 enabling it to be clamped and held in position during its locking by means of a counter nut 129.
  • the counter nut 129 has a tool socket 111 for clamping.
  • the tool socket 111 is provided so that the locknut 129 can be tightened while maintaining the cylindrical support 102 by means of its tool holder 109.
  • cylindrical support 102 and its counter nut 129 screwed into the threaded hole 101 of the engine block 100 constitute a device for adjusting the functional clearances of the transmission device 1 in the engine block 100.
  • cylindrical support 102 can be secured to a thick plate, not shown, fixed from the outside to the motor block 100 by means of screws.
  • the adjustment of the functional clearances of the transmission device 1 in the engine block 100 is achieved by means of a shim, not shown.
  • This shim arranged between the thick plate and the motor block 100, adjusts the distance between said plate and said motor unit.
  • the cavity 28 in sphere portion serving as a housing for the cap 31 as a sphere portion of the support piece 76, can be arranged in the cylindrical support 102.
  • the flat face 32 of the support piece 76 slides on a flat face arranged on the control rack 7, that is to say, unlike that described above, without thereby changing the object of the present invention.
  • the second means consist of a pressure cylinder 62 whose piston 61 makes, thanks to a spherical profile, a connection of the ball-and-socket type between the control rack 7 and the engine block 100.
  • a distributor 65 makes it possible to carry out a permanent comparison of the pressures prevailing in the upper chambers 121 and lower 122 in order to connect the one having the highest pressure with the chamber 66 of the pressing ram 62.
  • the distributor 65 makes it possible to connect the upper chamber 121 or lower 122, the pressure of which is highest with the chamber 66 of the presser cylinder 62.
  • the pressure cylinder 62 comprises a spring 63 which makes it possible to keep the different members of the transmission device 1 in contact when the pressure prevailing in the chamber 66 is low.
  • the spring 63 may be helical or "belleville” type.
  • the distributor 65 can be housed in the thickness of the jack piston 13. In this case, it is connected to the pressing cylinder 62 by channels 64 arranged in the jack piston 13, the upper cylinder rods 10 and lower 16 and in the control rack 7.
  • the engine block 100 can be made of steel, cast iron or light alloy. It may include one or more dry or wet shirts. It may also comprise one or more cylinders 110 directly bored in said engine block 100.
  • the engine block 100 may comprise at least one channel and / or at least one chamber in which circulates a fluid which provides cooling of the engine.
  • the engine block 100 may comprise at least one channel and / or at least one chamber in which a lubricating fluid circulates the various components of the engine.
  • the motor unit 100 comprises bearing caps 141 fixed by at least two screws, said bearing caps 141 can be incorporated in a bearing housing 140.
  • the engine block 100 may comprise balancing shafts to limit the effect of the vibrations, said balancing shafts being able to be mounted in an independent housing fixed to the engine block 100.
  • the engine block 100 may comprise a lubricant housing. made either of stamped sheet metal, or of light alloy or plastic, comprising or not reinforcing structures.

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  • 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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Compressor (AREA)
  • Control Of Electric Motors In General (AREA)
EP05736556A 2004-03-11 2005-03-11 Dispositif de reglage pour moteur a rapport volumetrique variable Not-in-force EP1740810B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0402540A FR2867515B1 (fr) 2004-03-11 2004-03-11 Dispositif de reglage pour moteur a rapport volumetrique variable
US62418504P 2004-11-03 2004-11-03
PCT/FR2005/000584 WO2005098219A1 (fr) 2004-03-11 2005-03-11 Dispositif de reglage pour moteur a rapport volumetrique variable

Publications (2)

Publication Number Publication Date
EP1740810A1 EP1740810A1 (fr) 2007-01-10
EP1740810B1 true EP1740810B1 (fr) 2009-05-13

Family

ID=34896458

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05736556A Not-in-force EP1740810B1 (fr) 2004-03-11 2005-03-11 Dispositif de reglage pour moteur a rapport volumetrique variable

Country Status (12)

Country Link
US (1) US7562642B2 (es)
EP (1) EP1740810B1 (es)
JP (1) JP4601663B2 (es)
KR (1) KR101157279B1 (es)
CN (1) CN100458124C (es)
AT (1) ATE431497T1 (es)
AU (1) AU2005230535B2 (es)
CA (1) CA2558354C (es)
DE (1) DE602005014464D1 (es)
ES (1) ES2326748T3 (es)
FR (1) FR2867515B1 (es)
WO (1) WO2005098219A1 (es)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102400794A (zh) * 2011-11-21 2012-04-04 黄轩弟 一种变压缩比发动机
US10202899B2 (en) 2014-10-13 2019-02-12 MCE-5 Development S.A. Device for compensating for the operating clearances of an engine

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2896544B1 (fr) * 2006-01-26 2008-05-02 Vianney Rabhi Ensemble culasse et bloc moteur pour moteur a rapport volumetrique variable
FR2896538B1 (fr) * 2006-01-26 2008-05-02 Vianney Rabhi Dispositif electromecanique de commande d'un moteur a rapport volumetrique variable
FR2896539B1 (fr) * 2006-01-26 2008-05-02 Vianney Rabhi Dispositif presseur pour moteur a rapport volumetrique variable.
JP4645478B2 (ja) * 2006-02-28 2011-03-09 日産自動車株式会社 多気筒内燃機関の複リンク式ピストン−クランク機構及びその圧縮比調整方法。
DE602007006491D1 (de) 2006-07-07 2010-06-24 Borgwarner Inc Steuerverfahren für ein antriebssystem mit variabler verdichtung
FR2914950B1 (fr) * 2007-04-16 2012-06-15 Vianney Rabhi Dispositif permettant de mesurer directement sur le piston le rapport volumetrique effectif d'un moteur a taux de compression variable.
FR2914951B1 (fr) 2007-04-16 2012-06-15 Vianney Rabhi Dispositif electrohydraulique de pilotage en boucle fermee du verin de commande d'un moteur a taux de compression variable.
FR2919022B1 (fr) * 2007-07-19 2012-10-26 Vianney Rabhi Centrale hydraulique pour moteur a taux de compression variable.
FR2933140B1 (fr) * 2008-06-26 2011-11-11 Vianney Rabhi Dispositif de reglage du taux de compression a levee de bille pour moteur a taux de compression variable.
FR2933141B1 (fr) * 2008-06-27 2011-11-11 Vianney Rabhi Dispositif de levee de bille a vis pour moteur a taux de compression variable.
US8220422B2 (en) * 2009-08-25 2012-07-17 Manousos Pattakos Rack gear variable compression ratio engines
CN101672265B (zh) * 2009-10-12 2012-06-27 浙江鸿友压缩机制造有限公司 直线导向约束往复活塞式压缩机
FR2956452B1 (fr) * 2010-02-17 2012-04-06 Vianney Rabhi Compresseur a piston a double effet guide par un rouleau et entraine par une roue dentee et des cremailleres
US8251041B2 (en) * 2010-03-11 2012-08-28 West Virginia University Accelerated compression ignition engine for HCCI
KR101886078B1 (ko) * 2012-10-31 2018-08-08 현대자동차 주식회사 압축비 가변기구를 구비한 엔진
CN102953806A (zh) * 2012-11-19 2013-03-06 黎澄生 X-可变压缩比发动机
JP6283687B2 (ja) * 2012-12-21 2018-02-21 ボーグワーナー インコーポレーテッド 可変圧縮比ピストンシステム
CN105332798A (zh) * 2014-08-12 2016-02-17 刘玉华 一种t型连杆活塞发动机传动机构
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.
US10781903B2 (en) * 2017-11-14 2020-09-22 Tadatec, Llc Slider-crank mechanism for eliminating side forces
CN108104958B (zh) * 2017-12-15 2020-04-07 东风汽车集团有限公司 一种可变压缩比的发动机机构
FR3081928B1 (fr) * 2018-06-04 2021-01-15 MCE 5 Development Assemblage multifonctionnel incluant une platine de synchronisation pour le guidage d’un piston de combustion dans un moteur a taux de compression variable
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
CN110778397B (zh) * 2019-09-19 2021-05-18 潍柴动力股份有限公司 获取气缸垫片厚度的装置及方法
WO2021201618A1 (ko) * 2020-04-02 2021-10-07 장순길 가변 압축비 엔진
US11421588B2 (en) 2020-04-02 2022-08-23 Soon Gil Jang Variable compression ratio engine

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CN102400794A (zh) * 2011-11-21 2012-04-04 黄轩弟 一种变压缩比发动机
US10202899B2 (en) 2014-10-13 2019-02-12 MCE-5 Development S.A. Device for compensating for the operating clearances of an engine

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CN1950596A (zh) 2007-04-18
KR20060130243A (ko) 2006-12-18
CN100458124C (zh) 2009-02-04
JP2007538187A (ja) 2007-12-27
US20080017023A1 (en) 2008-01-24
WO2005098219A1 (fr) 2005-10-20
AU2005230535B2 (en) 2010-09-23
US7562642B2 (en) 2009-07-21
KR101157279B1 (ko) 2012-06-15
JP4601663B2 (ja) 2010-12-22
CA2558354C (fr) 2012-09-25
ATE431497T1 (de) 2009-05-15
EP1740810A1 (fr) 2007-01-10
FR2867515A1 (fr) 2005-09-16
ES2326748T3 (es) 2009-10-19
AU2005230535A1 (en) 2005-10-20
CA2558354A1 (fr) 2005-10-20
DE602005014464D1 (de) 2009-06-25
FR2867515B1 (fr) 2006-06-02

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