EP2646659B1 - An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine - Google Patents

An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine Download PDF

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Publication number
EP2646659B1
EP2646659B1 EP11805067.3A EP11805067A EP2646659B1 EP 2646659 B1 EP2646659 B1 EP 2646659B1 EP 11805067 A EP11805067 A EP 11805067A EP 2646659 B1 EP2646659 B1 EP 2646659B1
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EP
European Patent Office
Prior art keywords
pressure
gas exchange
opening
pressure medium
exchange valve
Prior art date
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Application number
EP11805067.3A
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German (de)
English (en)
French (fr)
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EP2646659A1 (en
Inventor
Ilari Kallio
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Wartsila Finland Oy
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Wartsila Finland Oy
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L11/00—Valve arrangements in working piston or piston-rod
    • F01L11/02—Valve arrangements in working piston or piston-rod in piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/02—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for reversing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means

Definitions

  • the present invention relates to an arrangement and a method of operating a gas exchange valve of an internal combustion engine.
  • the present invention relates also to a novel cylinder head and a new method of upgrading an internal combustion engine.
  • the gas exchange valves of the cylinders are controlled by a camshaft, which is, on the one hand, connected by means of a gear or chain or belt with the crankshaft of the engine so that it rotates with the crankshaft, and on the other hand, connected mechanically to the valves by means of push rods and rockers, mere rockers, or by direct contact between the camshaft cams and the valve stems.
  • a camshaft which is, on the one hand, connected by means of a gear or chain or belt with the crankshaft of the engine so that it rotates with the crankshaft
  • the inlet and outlet valves both have their respective camshafts.
  • the actuator needs to be dimensioned against the maximum imaginable opening force of a gas exchange valve in any operating condition.
  • the opening force is the product of the effective surface area of the actuator and the pressure of the hydraulic system connected to the actuator.
  • the hydraulic power consumed in opening a gas exchange valve is the product of the volume flow and the pressure of the hydraulic system.
  • a large effective surface area of the actuator leads to high volume flow and thus high power consumption in the system. In other words, the power consumption of a hydraulic actuator is constant irrespective of the force actually needed to open a gas exchange valve.
  • EP-B1-1 403 473 discusses a hydraulic valve actuation system.
  • the EP document discloses a hydraulic actuator used for operating a gas exchange valve of an internal combustion engine.
  • the hydraulic actuator has a body provided with an internal cavity housing a piston.
  • the piston is arranged at an axial end thereof in communication with a valve stem.
  • the piston has three coaxial cylindrical sections such that the diameter of the uppermost section (at an end opposite to the end communicating with the valve stem) is the smallest, the centre section having a largest diameter, and the lowermost having a diameter larger than that of the uppermost section but smaller than that of the centre section.
  • the piston sections form together with the internal cavity of the actuator body several coaxial chambers.
  • the effective cross sectional surface areas of the chambers are varying such that the surface area of the first chamber is the smallest, the surface area of the second annular chamber the largest, and the surface area of the third annular chamber smaller than that of the second annular chamber, but larger than that of the first chamber.
  • the chambers are connected by means of pressure conduits and valve means to a high pressure fluid supply and to a low pressure fluid supply except for the third annular chamber that is in constant flow communication with the high pressure fluid supply.
  • the operation of the hydraulic actuator is controlled by a control valve, which in its first position allows the pressurized fluid flow from the high pressure fluid supply to the second annular chamber.
  • the high pressure fluid acting on the largest surface area affects by opening the valve against the forces originating from the valve spring, from the high pressure fluid acting on the surface area in the third annular chamber, from the gas pressure in the cylinder of the internal combustion engine and the acceleration of the valve.
  • the control valve In its second position the control valve allows the communication of the second annular chamber with the low pressure fluid supply so that high pressure prevailing in the third annular chamber acting on the second largest surface area of the piston aids returns the piston up away from the valve.
  • the upper end of the piston i.e.
  • the first chamber is provided with means for dampening the movement of the piston upwards in order to slow down the speed the valve is closing so that the valve plate does not hit the valve seat too strongly when closing.
  • the first chamber is, for the dampening purpose, arranged in flow communication with both the high pressure and the low pressure fluid supply via specific valve arrangements. Thus the first chamber does not participate in the opening of the gas exchange valve, but merely slows down the final closing of the gas exchange valve.
  • the EP- document discusses also another piston structure for the hydraulic actuator.
  • the centre section of the piston is formed of two coaxial parts that are slidable in relation to each other.
  • the outer i.e. the second part of the piston is an annular sleeve arranged around the first part of the piston that is used for operating the valve stem.
  • the annular piston part rests against a shoulder on the first piston part, and in a second position (gas exchange valve open) the annular part rests against a shoulder on the chamber inner wall.
  • the actuator functions such that when the second annular chamber having the largest cross-sectional area i.e.
  • both piston parts move together i.e. the annular piston part resting on the shoulder on the first piston part aids in moving the piston downwards and in opening or unseating the gas exchange valve.
  • the annular piston part meets a shoulder on the chamber inner wall and stops whereby the first part of the piston continues to move downwards but now with a significantly smaller force due to a smaller effective area.
  • the above discussed prior art hydraulic actuator tries to reduce the energy consumption involved in operating the gas exchange valves.
  • the gained saving represents only a small improvement to earlier prior art hydraulic actuator systems.
  • What the hydraulic actuator of the above discussed EP- document in fact does is that it takes into account the pressure reduction in the combustion chamber immediately after the unseating of the gas exchange valve i.e. after lifting the valve plate off the seat surface.
  • the pressure in the combustion chamber is released, whereby the cylinder pressure does not resist the opening of the gas exchange valve any more, or at least significantly less, and the opening of the valve may be continued with a smaller force.
  • the EP- document teaches a hydraulic actuator structure that starts opening i.e.
  • a basis for the present invention is that the force required to operate a gas exchange valve of an internal combustion engine is not constant.
  • the force required to unseat and to open a gas exchange valve depends on several factors.
  • a first factor is the acceleration force i.e. the acceleration of the valve movement, which is proportional to the engine speed and to the masses of the gas exchange valve and the piston of the hydraulic actuator.
  • a second factor is the pressure difference over the valve plate, which has an effect up to the end of the unseating phase. The pressure difference is dependent on the engine operating conditions, i.e. on the engine load and crank angle.
  • a third factor is the force originating from the spring of the gas exchange valve (if such is used).
  • a fourth factor is fluid pressure (if any) in the actuator acting against the piston movement (third annular chamber in EP-B1-1 403 473 ).
  • a first object of the present invention is to overcome some weaknesses, drawbacks and problems of the prior art hydraulic actuators used for opening gas exchange valve/s of an internal combustion engine.
  • a second object of the present invention is to reduce the power consumption of a hydraulic actuator by adjusting the force used for opening a gas exchange valve to meet the demands the pressure difference over the valve plate sets for the force required to open a gas exchange valve.
  • a third object of the present invention is to be able to adjust the operation of a hydraulic actuator and its flow rate to meet the demands the engine speed sets to the valve opening/closing speed.
  • a fourth object of the invention is to offer a structurally simple hydraulic actuator, i.e. an actuator having minimum number of parts, the parts having very few surfaces to be machined and to be sealed, whereby the resulting actuator for opening gas exchange valve/s of an internal combustion engine is cheap, reliable and extremely adjustable.
  • a fifth object of the invention is to improve the reliability of the system.
  • a failure of one does not make the system unavailable, but only part of the system performance is lost.
  • the system can identify the failed component and be readjusted to failure mode.
  • a seventh object of the present invention is to offer simple and energy efficient means for repairing and upgrading/modernizing a state-of-the-art internal combustion engine having a camshaft and mechanical means in communication with the camshaft for operating the gas exchange valves.
  • An eighth object of the present invention is to offer a novel cylinder head for modernizing an internal combustion engine to meet today's demands for energy efficiency and emission control.
  • a ninth object of the invention is to offer a pressure medium actuator for operating a gas exchange valve of an internal combustion engine.
  • the actuator may be not only hydraulic, but also pneumatic.
  • an arrangement for operating a gas exchange valve of an internal combustion engine comprising:
  • At least an object of the invention is achieved by the method of operating a gas exchange valve of an internal combustion engine by means of the above described arrangement so that
  • At least an object of the invention is met by a cylinder head of an internal combustion engine, the cylinder head comprising at least two gas exchange valves and means for operating the gas exchange valves, wherein at least one means for operating a gas exchange valve is the arrangement in accordance with one or more of the apparatus claims.
  • At least an object of the invention is met by a method of upgrading an internal combustion engine with a cylinder head with at least one gas exchange valve, and mechanical gas exchange valve operating means, wherein mechanical gas exchange valve operating means is replaced with the arrangement in accordance with one or more of the apparatus claims.
  • the present invention when solving at least some of the above-mentioned problems, also brings about a number of advantages, of which a few has been listed in the following.
  • the pressure medium actuator of the present invention :
  • Figure 1 illustrates an axial cross sectional view of a pressure medium actuator 10.
  • the actuator 10 has a body 12 including an internal cavity extending from the vicinity of an end 14 of the body to the opposite end 16 of the body 10.
  • the end 16 of the body is provided with a cover 18, which is provided with a preferably central opening 20.
  • the internal cavity is formed of several cylindrical wall portions 22, 24 and 26 such that the diameters of the wall portions grow towards the end of the body having the cover 18.
  • the pressure medium actuator 10 has a unitary piston 30, whose shape corresponds substantially to that of the internal cavity of the body 12.
  • the unitary piston is formed, in this embodiment, of four cylindrical sections 32, 34, 36 and 38, which have been arranged axially one on top of the other.
  • the uppermost section 32 of the piston 30 has a diameter that corresponds to the diameter of the wall portion 22 leaving, however, a sufficient running clearance therebetween.
  • the second section 34 of the piston 30 has a diameter corresponding to that of wall portion 24, and the third section 36 of the piston has a diameter that corresponds to that of the third wall portion 26.
  • the fourth section 38 of the piston 30 has a diameter that corresponds to that of the central opening 20 in the cover 18.
  • the piston 30 and the internal cavity of the body 12 of the pressure medium actuator form pressure chambers 40, 42, 44 and 46.
  • the chamber 40 is limited by the wall portion 22, the end surface of the internal cavity and the end surface 48 of the first section 32 of the piston 30.
  • the chamber 42 is limited by the wall portion 24, a cylindrical side surface of the first section 32 of the piston 30, the annular end surface 50 of the second section 34 of the piston 30, and the shoulder surface between the first 22 and second wall portions 24 of the internal cavity.
  • the chamber 44 is limited by the wall portion 26, a cylindrical side surface of the second section 34 of the piston 30, the annular end surface 52 of the third section 36 of the piston 30, and the shoulder surface between the second 24 and third wall portions 26 of the internal cavity.
  • the chamber 46 is limited by the wall portion 26, a cylindrical side surface of the fourth section 38 of the piston 30, the lower annular end surface 54 of the third section 34 of the piston 30, and the surface of the cover 18 facing to the internal cavity.
  • the effective surfaces affecting the movement of the piston 30, and the valve stem 100 arranged in communication with the piston 30 are the end surface 48 in pressure chamber 40, the annular end surface 50 in pressure chamber 42, the annular end surface 52 in pressure chamber 44, and the annular end surface 54 in pressure chamber 46.
  • the pressure chambers 40, 42 and 44 may be called opening pressure chambers, and the pressure chamber 46 a closing pressure chamber.
  • the effective surfaces 48, 50 and 52 may be called opening surfaces and surface 54 a closing surface.
  • a preferred, though not necessary, feature of the present invention is that the areas of the effective surfaces form a geometric series such that the area of surface 48 is A, the area of surface 50 is 2*A and the area of surface 52 is 4*A.
  • the purpose of arranging the areas to form such a geometric series will be explained in more detail later on.
  • the pressure medium actuator body 12 and piston 30 form a first part of the pressure medium valve operating arrangement.
  • the second part of the operating arrangement is formed of a tank 61 (when it is a question of a hydraulic actuator), a pressure medium supply 70, first control valves 80, 82, 84 and 86, conduits 72, 74, 76 and 78, seconds control valves 90, 92, 94 and 96 with conduits 62, 64, 66 and 68.
  • the conduits 72 - 78 connect the pressure medium supply via the first control valves 80 - 86 to the pressure chambers 40 - 46.
  • the pressure chambers 40 - 46 are connected by means of second control valves 90, 92, 94 and 96 and conduits 62 - 68, and pressure outlet 60 to the tank 61.
  • each pressure chamber has one first control valve and one second control valve for controlling the operation of the chamber.
  • the control valves 80 - 86, and 90 - 96 are preferably solenoid valves or some other electrically operable valves that are connected to a control unit (CU) such that the control unit (CU), based on input from the engine control unit, is able to open and close each valve independently.
  • a solenoid operated control valve works normally such that it is closed when the control unit (CU) does not allow electric current enter the solenoid.
  • the first control valves 80 - 86 have been shown here as two-position, two-way valves, i.e.
  • control valves 90 - 96 have been shown as two-position, two-way valves that either open or block a flow connection between a pressure chamber 40 - 46 and the tank 61.
  • Figure 1 illustrates the pressure connections i.e. positions of the control valves when the counter pressure prevailing in the combustion chamber of a cylinder of an internal combustion engine is at its lowest whereby the force needed to open the gas exchange valve 102 is the lowest possible.
  • control valve 80 connects the pressure chamber 40 to the pressure medium supply 70 via conduit 72, whereas the other three control valves 82, 84 and 86 are closed.
  • control valve 90 is kept closed whereby it cuts the connection from pressure chamber 40 along conduits 62 and 60 to the tank 61 and allows the pressure of the pressure medium source affect on the effective piston surface 48.
  • the other control valves 92, 94 and 96 connect their respective pressure chambers 42, 44 and 46 to the tank 61.
  • the high pressure medium acting on the piston surface 48 affects the opening of the gas exchange valve 102, and simultaneously compresses the valve spring 104 and forces the medium in pressure chamber 46 to the tank 61.
  • FIG. 2 illustrates an operating phase of the pressure medium actuator i.e. the positions of the control valves when the gas exchange valve is to be closed.
  • the control valve 86 connects the pressure chamber 46 via conduit 78 to the pressure medium supply 70 whereas the rest three control valves 80, 82 and 84 are closed.
  • the second control valves are operated such that three of them, i.e. the control valves 90, 92 and 94 connect their respective pressure chambers 40, 42 and 44 to the tank 61, and the control valve 96 being in communication with the pressure chamber 46 to be pressurized is closed.
  • the high pressure medium acting on effective piston surface 54 moves the piston upwards allowing the gas exchange valve to close and forcing the medium from pressure chambers 40, 42 and 44 to the tank 61.
  • the pressure medium actuator of the present invention may also be operated such that the piston is stopped at any desired position by using the control valves. For instance the upward movement of the piston, as well as that of the gas exchange valve may be stopped by closing the second valves 90, 92 and 94, and keeping the first valves 80 - 84 closed, too.
  • Figure 3 illustrates such an operating phase of the pressure medium actuator i.e. the positions of the control valves when the force required to open the gas exchange valve is clearly higher than that in the phase shown in Figure 1 .
  • control valves 80 and 84 connect their respective pressure chambers 40 and 44 to the pressure medium supply 70, whereas control valves 82 and 86 are closed.
  • valves 90 and 94 are closed allowing the medium pressure act in the pressure chambers 40 and 44 on effective surfaces 48 and 52 (reference numerals shown in Figure 1 ).
  • Control valves 92 and 96 connect their respective pressure chambers 42 and 46 to the tank 61. In this case the force used for opening the valve is 5-fold compared to the example of Figure 1 .
  • Figure 3 illustrates as a schematical, additional and exemplary arrangement a conduit 98, which has been arranged such that, for instance, when closing the gas exchange valve, the pressure chamber 42 may be emptied via both control valve 92 and control valve 94.
  • the speed of the actuator piston may be adjusted as, if the piston is supposed to move upwards, and only control valves 90 and 94 are open, and control valve 92 closed the medium from both pressure chambers 42 and 44 has to pass control valve 94.
  • the flow rate of a control valve 94 is limited the additional flow (compared to normal situation when each pressure chamber is discharged via its control valve) from pressure chamber 42 increases the total flow and reduces the speed the piston may move.
  • the conduit 98 may be a valve arrangement with which the outlet flow from chamber 42 may be directed to either control valve 92, to control valve 94 or both, and/or outlet flow from chamber 44 may be directed to either control valve 94, to control valve 92 or both.
  • a conduit, or valve arrangement may be arranged freely at the outlet side of the actuator body. It would even be possible, in the embodiment of Figure 3 , that the medium flow from any pressure chamber 40 - 44 could be directed to one, two or three second control valves 90 - 94, whereby the adjustability of the speed of the piston movement would be maximized.
  • the closing phase of the gas exhaust valve it is possible, in the closing phase of the gas exhaust valve, to first allow the pressure medium from the pressure chambers be discharged via their 'own' control valves i.e. via all three control valves, then close one of the control valves 90 - 94, and allow the pressure medium be discharged via two control valves whereby the valve closing speed is slowed down. In the next stage one more control valve is closed, and the discharge of all pressure chambers 40 - 44 takes place via one control valve, until it is closed, too, stopping the valve, and piston, movement.
  • the present invention makes it possible to adjust stepwise the force used for opening a gas exchange valve.
  • the following table lists the various combinations of the positions of the first control valves and the resulting forces when opening the gas exchange valve.
  • the control valve 86 is always closed, and control valve 96 is, always connecting chamber 46 to the tank 61 (unless some damping effect is desired).
  • the second control valves 90 - 94 their position depends on the positions of the corresponding first control valves 80 - 84, respectively. It means that when a first control valve is in 'open' position, the corresponding (connected to the same pressure chamber) second control valve is in 'closed' position, and vice versa.
  • Chamber 40 (area A) connected to Chamber 42 (area 2*A) connected to Chamber 44 (area 4*A) connected to Force Pressure fluid supply/ Valve 80 open Pressure outlet/Valve 92 open Pressure outlet/Valve 94 open F Pressure outlet/Valve 90 open Pressure fluid supply/ Valve 82 open Pressure outlet/Valve 94 open 2*F Pressure fluid supply/ Valve 80 open Pressure fluid supply/ Valve 82 open Pressure outlet/Valve 94 open 3*F Pressure outlet/Valve 90 open Pressure outlet/Valve 92 open Pressure fluid supply/ Valve 84 open 4*F Pressure fluid supply/ Valve 80 open Pressure outlet/Valve 92 open Pressure fluid supply/ Valve 84 open 5*F Pressure outlet/Valve 90 open Pressure fluid supply/ Valve 82 open Pressure fluid supply/ Valve 84 open 6*F Pressure fluid supply/ Valve 80 open Pressure fluid supply/ Valve 82 open Pressure fluid supply/ Valve 84 open 7*F
  • this exemplary pressure medium actuator is capable of being switched between 7 different force levels in accordance with the requirements of the gas exchange valve.
  • Factors having an influence on the used force i.e. the chosen combination of control valve positions is dependent on the cylinder load, crank angle and engine speed, just to name a few factors.
  • the pressure medium actuator may have more or fewer (however, at least two) pressure chambers active in opening a gas exchange valve than the three pressure chambers 40, 42 and 44 shown in the above embodiment.
  • the number of applicable force levels decreases to three, and if there are four active pressure chambers, the number of force levels increases to 15 (1+2+4+8).
  • the pressure medium operated gas exchange valve actuator has two or more pressure chambers with effective surface areas A1, A2, ... An, of which one or more can be independently, electronically connected to the pressure medium supply.
  • a preferred way to select the effective surface areas of the pressure chambers is a geometric series, A, 2*A, 4*A..., but also other modes may be applied.
  • Figure 4 illustrates yet another preferred embodiment of the present invention.
  • the pressure medium actuator is provided with another pressure medium supply 70' that has been connected via an additional control valve 104 further to the system.
  • the pressure medium supply 70' has a pressure different from that of the pressure medium supply 70.
  • the first pressure medium supply 70 has been provided with an additional control valve 102 of its own. Both control valves 102 and 104 have been connected to the control unit (CU).
  • CU control unit
  • Figure 4 shows how, by means of the control valve 102, the pressure medium from supply 70 may be delivered depending in the position of the valves 80 - 86 to pressure chambers 40 - 46, and by means of the control valve 104, the pressure medium from the additional pressure medium supply 70' may be delivered depending in the position of the valves 80 - 86 to pressure chambers 40 - 46.
  • the purpose of adding another pressure medium supply and of arranging separate control valves for the both pressure medium supplies is to be able to control the opening force of the gas exchange valve better.
  • the additional pressure medium supply 70' to be connectable to one or more first control valves 80 - 86, whereby only those valves (and the pressure chambers connected thereto) could utilize the different pressure available in the supply 70'.
  • an another pressure medium supply 70' having a pressure different from that of pressure medium supply 70 the number of different force levels achievable by the pressure medium actuator are doubled.
  • a digital flow control unit 110 that may, optionally, be used to replace one or more of the control valves 80, 82, 84 and 86, as well as one or more of the control valves 90 - 96 has been illustrated.
  • the flow control unit 110 comprises two or more digital valves 112, 114, 116 connected in parallel. Each valve is designed for a certain flow rate at certain pressure differential.
  • the flow rates of different valves can be different. For instance such that the flow rate of the first valve 112 is V, the flow rate of the second valve 114 is 2*V, the flow rate of the third valve 4*V, and the flow rate of n'th valve 2 (n-1) *V.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Pressure Circuits (AREA)
EP11805067.3A 2010-11-30 2011-11-29 An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine Active EP2646659B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20106256A FI20106256A0 (fi) 2010-11-30 2010-11-30 Järjestelmä ja menetelmä polttomoottorin kaasunvaihtoventtiilin käyttämiseksi, sylinterinkansi ja menetelmä polttomoottorin uudistamiseksi
PCT/FI2011/051054 WO2012072878A1 (en) 2010-11-30 2011-11-29 An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2646659A1 EP2646659A1 (en) 2013-10-09
EP2646659B1 true EP2646659B1 (en) 2015-08-05

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Application Number Title Priority Date Filing Date
EP11805067.3A Active EP2646659B1 (en) 2010-11-30 2011-11-29 An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine

Country Status (5)

Country Link
EP (1) EP2646659B1 (zh)
KR (1) KR101657752B1 (zh)
CN (1) CN103228878B (zh)
FI (1) FI20106256A0 (zh)
WO (1) WO2012072878A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11566545B2 (en) 2019-05-02 2023-01-31 Caterpillar Inc. Cam actuated gas admission valve with electro-hydraulic trim control

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE2010291A1 (de) * 1970-03-05 1971-09-23 Robert Bosch Gmbh, 7000 Stuttgart Steuerung von Ein- und Auslaßventilen bei Brennkraftmaschinen durch Flüssigkeit
DE10143959A1 (de) * 2001-09-07 2003-03-27 Bosch Gmbh Robert Hydraulisch gesteuerter Aktuator zur Betätigung eines Ventils
DE10230478A1 (de) 2002-07-06 2004-01-15 Robert Bosch Gmbh Vorrichtung zur Steuerung von Gaswechselventilen
JP2004084670A (ja) * 2002-08-28 2004-03-18 Man B & W Diesel As 水圧で作動されるバルブ
US6899068B2 (en) 2002-09-30 2005-05-31 Caterpillar Inc Hydraulic valve actuation system
EP1536107A1 (en) * 2003-11-28 2005-06-01 Thomas Friedhelm Buschkuehl Valve operating apparatus and method for an engine
US7341028B2 (en) * 2004-03-15 2008-03-11 Sturman Industries, Inc. Hydraulic valve actuation systems and methods to provide multiple lifts for one or more engine air valves
US7665431B2 (en) * 2006-10-11 2010-02-23 Gm Global Technology Operations, Inc. Drive piston assembly for a valve actuator assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11566545B2 (en) 2019-05-02 2023-01-31 Caterpillar Inc. Cam actuated gas admission valve with electro-hydraulic trim control

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Publication number Publication date
FI20106256A0 (fi) 2010-11-30
CN103228878A (zh) 2013-07-31
KR101657752B1 (ko) 2016-09-19
EP2646659A1 (en) 2013-10-09
KR20130121909A (ko) 2013-11-06
WO2012072878A1 (en) 2012-06-07
CN103228878B (zh) 2015-06-24

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