EP2834480B1 - Hydraulic actuator and gas exchange valve arrangement - Google Patents

Hydraulic actuator and gas exchange valve arrangement Download PDF

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Publication number
EP2834480B1
EP2834480B1 EP13711447.6A EP13711447A EP2834480B1 EP 2834480 B1 EP2834480 B1 EP 2834480B1 EP 13711447 A EP13711447 A EP 13711447A EP 2834480 B1 EP2834480 B1 EP 2834480B1
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EP
European Patent Office
Prior art keywords
valve
pressurizing chamber
actuator
drive piston
input portion
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.)
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Application number
EP13711447.6A
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German (de)
English (en)
French (fr)
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EP2834480A1 (en
Inventor
Saku Niinikangas
Magnus Sundsten
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.)
Wartsila Finland Oy
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Wartsila Finland Oy
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Publication of EP2834480A1 publication Critical patent/EP2834480A1/en
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Publication of EP2834480B1 publication Critical patent/EP2834480B1/en
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    • 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

Definitions

  • the present invention relates to a hydraulic actuator for opening a gas exchange valve of an internal combustion engine according to the preamble of claim 1.
  • the invention also concerns a gas exchange valve arrangement in accordance with the other independent claim.
  • valves In large internal combustion engines, such as in ship or power plant engines, the gas exchange valves can be either mechanically or hydraulically actuated.
  • the most conventional way to operate the intake and exhaust valves is to use cam-driven valve opening mechanisms, where the valves are opened by the lobe of a rotating cam and closed by valve springs.
  • cam-driven valve opening mechanisms where the valves are opened by the lobe of a rotating cam and closed by valve springs.
  • An object of the present invention is to provide an improved hydraulic actuator for opening a gas exchange valve of an internal combustion engine.
  • the characterizing features of the actuator according to the present invention are given in the characterizing part of claim 1.
  • Another object of the invention is to provide an improved gas exchange valve arrangement.
  • the characterizing features of the gas exchange valve arrangement according to the invention are given in the characterizing part of the other independent claim.
  • the hydraulic actuator comprises a pressurizing chamber for pressurizing hydraulic fluid, a drive piston that is arranged in the pressurizing chamber and which drive piston divides the pressurizing chamber into at least one input portion and at least one output portion, an inlet duct for introducing pressurized hydraulic fluid into the input portion of the pressurizing chamber for moving the drive piston, a fluid outlet for supplying hydraulic fluid from the output portion of the pressurizing chamber to the gas exchange valve, and an outlet duct for releasing hydraulic fluid from the input portion of the pressurizing chamber.
  • the actuator further comprises a hydraulic valve having a first position, in which position flow from the inlet duct to the input portion of the pressurizing chamber is allowed and flow from the input portion to the outlet duct is prevented, and a second position, in which position flow from the inlet duct to the input portion of the pressurizing chamber is prevented and flow from the input portion to the outlet duct is allowed.
  • the gas exchange valve arrangement comprises at least one gas exchange valve for opening and closing flow communication between a gas exchange duct and a cylinder of the engine, the gas exchange valve comprising a valve head and a valve stem, a receiving chamber, a driven piston that is in mechanical connection with the valve stem and arranged in the receiving chamber, and a hydraulic actuator defined above.
  • the number of electrical components in the gas exchange valve actuating mechanism can be minimized.
  • the actuator and the arrangement thus combine the reliability of a mechanical valve opening system and the flexibility of an electro-hydraulic system. Since the valve lift is limited by the stroke of the drive piston, too high valve lifts are prevented.
  • the actuator comprises a control valve for actuating the hydraulic valve.
  • the drive piston divides the output side of the pressurizing chamber into a first output portion that is provided with a first fluid outlet and into a second output portion that is provided with a second fluid outlet.
  • Each of the fluid outlets can be used for supplying hydraulic fluid to one gas exchange valve. This guarantees simultaneous opening of both gas exchange valves.
  • the output portion end of the drive piston is formed of a solid cylindrical part and the input portion end of the drive piston is formed of a hollow cylindrical part that comprises at least one opening in the sleeve for allowing flow into and out of the input portion of the pressurizing chamber.
  • the opening can comprise a groove that is arranged around the outer circumference of the hollow cylindrical part and a boring connecting the groove to the space defined by the hollow cylindrical part. Because of the groove, flow into the input portion of the pressurizing chamber or out of it is allowed in any angular position of the drive piston.
  • the actuator comprises means for throttling the flow into the input portion of the pressurizing chamber and/or out of the input portion at the beginning and/or at the end of the movement of the drive piston.
  • the throttling effect can be achieved by arranging the opening of the piston to be only partially aligned with the end of an intermediate duct connecting the input portion of the pressurizing chamber to the hydraulic valve when the drive piston is at the input portion end and/or at the output portion end of the pressurizing chamber.
  • the inlet duct and the outlet duct are provided with adjustable throttles for regulating flow rates in the ducts.
  • adjustable throttles gas exchange valve opening and closing speeds can be changed.
  • the actuator comprises a second drive piston that has a larger diameter and a shorter stroke than the first drive piston and which second drive piston is arranged in the input portion of the pressurizing chamber for assisting the first drive piston at the beginning of the pressurizing stroke.
  • the second drive piston With the second drive piston, the needed hydraulic pressure is lower and energy can be saved.
  • a fluid chamber that is in fluid communication with the inlet duct is arranged at one end of the spindle of the hydraulic valve, and a control valve is arranged to release pressure from the fluid chamber for actuating the hydraulic valve. No external fluid supply duct is thus needed for actuating the hydraulic valve.
  • the gas exchange valve arrangement is provided with a pressure accumulator that is connected to the outlet duct for recovering energy from the outlet duct, and to the inlet duct for supplying energy into the inlet duct.
  • the driven piston is arranged around the valve stem. This saves space compared to a construction where the driven piston is arranged at the end of the valve stem.
  • the hydraulic actuator and the gas exchange valve arrangement according to the invention can be used in large internal combustion engines, such as in main or auxiliary engines of ships or in engines that are used at power plants for producing electricity.
  • the arrangement comprises at least one gas exchange valve 1, 1', which opens and closes flow communication between a gas exchange duct 2 and a cylinder of the engine.
  • the gas exchange valves 1, 1' can be either intake valves or exhaust valves, and the gas exchange duct 2 is thus either an intake duct or an exhaust duct.
  • the arrangement comprises a first gas exchange valve 1 and a second gas exchange valve 1'.
  • each cylinder of the engine is provided with a gas exchange valve arrangement according to the invention.
  • the gas exchange valves 1, 1' are arranged in the cylinder head 4 of the respective cylinder.
  • Each gas exchange valve 1, 1' comprises a valve stem 1 b, 1b' and a valve head 1a, 1a'.
  • the valve head 1a, 1a' co-operates with a corresponding valve seat 1d, Id'.
  • a valve spring 16, 16' is arranged around the valve stem 1b, 1b' of each gas exchange valve 1, 1' for closing the gas exchange valve 1, 1'.
  • the cylinder head 4 is provided with valve guides 17, 17' for accommodating the gas exchange valves 1, 1'.
  • each gas exchange valve arrangement comprises a hydraulic actuator 35.
  • the hydraulic actuator 35 comprises a pressurizing chamber 9, in which a drive piston 7 is arranged.
  • the drive piston 7 divides the pressurizing chamber 9 into at least one input portion 9a and at least one output portion 9b.
  • the pressurizing chamber 9 is divided into one input portion 9a and into a first and a second output portion 9b, 9b'.
  • the drive piston 7 can reciprocate in the pressurizing chamber 9. When pressure medium is introduced into the input portion 9a of the pressurizing chamber 9, the drive piston 7 pressurizes hydraulic fluid on the output side 9b, 9b' of the pressurizing chamber 9.
  • a returning spring 18 is arranged in the pressurizing chamber 9 for pushing the drive piston 7 towards the input portion 9a of the pressurizing chamber 9.
  • the hydraulic actuator 35 comprises a hydraulic valve 10 for opening and closing flow communication between a pressure source, such as a hydraulic pump 12, and the input portion 9a of the pressurizing chamber 9.
  • the hydraulic valve 10 also prevents and allows outflow from the input portion 9a of the pressurizing chamber 9.
  • the hydraulic valve 10 is arranged between a hydraulic pump 12 and the input portion 9a of the pressurizing chamber 9.
  • the hydraulic actuator 35 further comprises fluid outlets 9d, 9d' for supplying hydraulic fluid from the output portions 9b, 9b' of the pressurizing chamber 9 to the gas exchange valves 1, 1'.
  • a driven piston 1c, 1c' is arranged in mechanical connection with the valve stem 1b, 1b' of each gas exchange valve 1, 1'.
  • the gas exchange valve 1, 1' is thus moved together with the driven piston 1c, 1c'.
  • the driven piston 1c, 1c' is arranged in a receiving chamber 5, 5' that is in fluid communication with the output portion 9b, 9b' of the pressurizing chamber 9.
  • the first output portion 9b of the pressurizing chamber 9 is connected with a first connecting duct 6 to the receiving chamber 5 of the first gas exchange valve 1, and the second output portion 9b' of the pressurizing chamber 9 is connected with a second connecting duct 6' to the receiving chamber 5' of the second gas exchange valve 1'. Since the hydraulic actuator 35 is provided with an own output portion 9b, 9b' for each of the gas exchange valves 1, 1', the pressurized hydraulic fluid is supplied simultaneously to both of the gas exchange valves 1, 1'.
  • an intermediate duct 20 is arranged between the hydraulic valve 10 and the pressurizing chamber 9 for connecting the input portion 9a of the pressurizing chamber 9 to the hydraulic valve 10.
  • the hydraulic valve 10 is a hydraulically actuated slide valve.
  • the hydraulic valve 10 is a three-way valve that comprises a first port 10a that is connected to the inlet duct 15, a second port 10b that is connected to the outlet duct 21, and a third port 10c that is connected to the intermediate duct 20.
  • the hydraulic valve 10 comprises a spindle 22 that has a first position and a second position. In the first position of the spindle 22, flow communication between the first port 10a and the third port 10c is closed and flow communication between the second port 10b and the third port 10c is open.
  • Hydraulic fluid can thus flow from the inlet duct 15 into the intermediate duct 20, but flow from the intermediate duct 20 into the outlet duct 21 is prevented.
  • flow communication between the first port 10a and the third port 10c is open and the flow communication between the second port 10b and the third port 10c is closed. Hydraulic fluid can thus flow from the intermediate duct 20 into the outlet duct 21, but flow from the inlet duct 15 into the intermediate duct 20 is prevented.
  • the hydraulic valve 10 is provided with a spring 19 that keeps the spindle 22 in the first position when the hydraulic valve 10 is not actuated. When an external force is applied to the spindle 22, the spindle 22 is moved to the second position.
  • the hydraulic actuator 35 is provided with a control valve 11.
  • the control valve 11 is a hydraulic valve that is operated with a solenoid.
  • the control valve 11 could also be some other kind of electrically actuated valve.
  • hydraulic fluid is introduced onto a pressure surface 23 of the spindle 22 for moving the spindle 22.
  • the receiving chamber 5, 5' is arranged around the valve stem 1b, 1b' and the driven piston 1c, 1c' is a projection of the valve stem 1b, 1b'. This arrangement enables compact design of the cylinder head 4.
  • the output portion end of the drive piston 7 is formed a solid cylindrical part 7b and the input portion end of the drive piston 7 is formed of a hollow cylindrical part 7a.
  • the input portion end of the solid cylinder 7b forms a surface onto which the pressure of the hydraulic fluid is applied.
  • the hydraulic fluid is introduced into the input portion 9a of the pressurizing chamber 9 through the sleeve of the hollow cylinder 7a.
  • the sleeve is therefore provided with at least one opening, which consists of a groove 13a and a drilling 13b.
  • two drillings 13b are in connection with the groove 13a. Because of the groove 13a that is arranged around the whole outer circumference of the hollow cylinder, flow through the drillings 13b is allowed in any angular position of the drive piston 7.
  • the groove 13a widens towards the outer surface of the hollow cylinder and is only partially aligned with the intermediate duct 20 when the drive piston 7 is at the input portion end of the pressurizing chamber 9. Therefore, the flow into the input portion 9a of the pressurizing chamber 9 is throttled when the hydraulic valve 10 is moved into the second position and fluid supply from the hydraulic pump 12 into the pressurizing chamber 9 is allowed. Consequently, the drive piston 7 accelerates smoothly.
  • the groove 13a becomes fully aligned with the intermediate duct 20 and maximum flow into the input portion 9a of the pressurizing chamber 9 is allowed.
  • the groove 13a becomes again partly overlapping with the walls of the pressurizing chamber 9.
  • FIG 7 is shown part of a valve actuator 35, where the opening of the drive piston is a straight drilling 13b.
  • the intermediate duct 20 between the hydraulic valve 10 and the input portion 9a of the pressurizing chamber 9 is connected to a groove 13c that encircles the inner surface of the pressurizing chamber 9.
  • the drilling 13b of the drive piston 7 is only partially aligned with the groove 13c of the input portion 9a of the pressurizing chamber 9. The flow out of the input portion 9a of the pressurizing chamber 9 or into it is thus throttled.
  • the groove 13c is chamfered so that the flow area is very small at the beginning and at the end of the movement of the drive piston 7.
  • the drive piston 7 further comprises a boring 39, which connects the input portion 9a of the pressurizing chamber 9 to the output portion 9b.
  • a second boring 40 connects the input portion 9a to the second output portion 9b'.
  • the input portion 9a and the output portions 9b, 9b' of the pressurizing chamber 9 are also provided with air removal ports 41, 42, 43 for removing air from the hydraulic system.
  • the diameters of the air removal ports 41, 42, 43 are small for preventing excessive leakage of the hydraulic fluid.
  • the air removal ports 41, 42, 43 can also be provided with throttles 41a, 42a, 43a for reducing leaking of the hydraulic fluid, as shown in figure 4 .
  • the embodiment shown in figure 3 differs from the embodiment of figures 1 and 2 in terms of the construction of the hydraulic valve 10.
  • the hydraulic valve 10 of figure 3 comprises a fourth port 10d.
  • the hydraulic actuator 35 comprises a first intermediate duct 20 and a second intermediate duct 28.
  • the first port 10a of the hydraulic valve 10 is connected to the inlet duct 15 and the third port 10c is connected to the first intermediate duct 20.
  • the second port 10b is connected to the outlet duct 21 and the fourth port 10d is connected to the second intermediate duct 28.
  • the spindle 22 allows flow from the inlet duct 15 into the first intermediate duct 20 and prevents flow from the second intermediate duct 28 into the outlet duct 21.
  • the spindle 22 allows flow from the second intermediate duct 28 into the outlet duct 21 and prevents flow from the inlet duct 15 into the second intermediate duct 28.
  • Hydraulic fluid is introduced into the input portion 9a of the pressurizing chamber 9 through the first intermediate duct 20.
  • the hydraulic fluid is released from the input portion 9a of the pressurizing chamber 9 through the second intermediate duct 28.
  • separate fluid supply to the control valve 11 is not needed.
  • the inlet duct 15 is connected with a control duct 26 to a fluid chamber 27 that is arranged at one end of the spindle 22. Together with the spring 19 of the hydraulic valve 10, the pressure in the fluid chamber 27 keeps the hydraulic valve 10 in the first position, when the control valve 11 is closed.
  • the driven piston 1c, 1c' is arranged at the end of the valve stem 1b, 1b'.
  • the hydraulic valve 10 is identical to the hydraulic valve 10 of figure 3 .
  • the first and the second intermediate ducts 20, 28 are merged into a combined intermediate duct 36 before the pressurizing chamber 9.
  • a third intermediate duct 37 and a fourth intermediate duct 38 are branched from the combined intermediate duct 36 and connected to the input portion 9a of the pressurizing chamber 9.
  • the diameters of the third intermediate duct 37 and the fourth intermediate duct 38 are smaller than the diameter of the combined intermediate duct 36.
  • the third and the fourth intermediate ducts 37, 38 are provided with check valves 24, 25. Through the third intermediate duct 37, flow from the combined intermediate duct 36 into the pressurizing chamber 9 is allowed.
  • the third intermediate duct 37 is located so that when the drive piston 7 is at the input portion end of the pressurizing chamber 9, the groove 13a of the drive piston 7 is aligned with the end of the third intermediate duct 37 and direct flow from the combined intermediate duct 36 into the pressurizing chamber 9 is prevented.
  • the fourth intermediate duct 38 flow from the pressurizing chamber 9 into the combined intermediate duct 36 is allowed.
  • the fourth intermediate duct 38 is located so that when the drive piston 7 is at the output portion end of the pressurizing chamber 9, the opening 13a of the drive piston 7 is aligned with the fourth intermediate duct 38 and direct flow from the pressurizing chamber 9 into the combined intermediate duct 36 is prevented.
  • the inlet duct 15 is provided with an adjustable throttle 30.
  • the outlet duct 21 is provided with an adjustable throttle 31.
  • the input portion 9a of the pressurizing chamber 9 is provided with a second drive piston 7'.
  • the second drive piston 7' has larger diameter and a shorter stroke than the first drive piston 7. Since the second drive piston 7' assists the first drive piston 7, smaller hydraulic pressure is needed at the beginning of the stroke of the first drive piston 7. Smaller hydraulic pressure decreases energy consumption of the arrangement.
  • the embodiment of figure 5 differs from the embodiment of figure 4 in that the arrangement is provided with a pressure accumulator 32 for energy recovery.
  • the pressure accumulator 32 is connected to the outlet duct 21 upstream from the throttle 31.
  • the pressure accumulator 32 is also connected to the inlet duct 15 upstream from the throttle 30 and downstream from the hydraulic pump 12 and the pressure accumulator 32.
  • a second hydraulic pump 12b is arranged downstream from the hydraulic pump 12 and from the pressure accumulator 32
  • a check valve 33 is arranged between the pressure accumulator 32 and the outlet duct 21 for preventing flow from the first hydraulic pump 12 or the pressure accumulator 32 into the outlet duct 21.
  • the first hydraulic pump 12 supplies hydraulic fluid at a smaller pressure level than is needed for operating the drive piston 7.
  • the pressure of the flow from the first hydraulic pump 12 and from the pressure accumulator 32 is raised to the sufficient level by the second hydraulic pump 12b.
  • the hydraulic valve 10 is a solenoid valve. Since the flow capacity of a single solenoid valve is small, the arrangement is provided with a second solenoid valve 10b that is arranged in parallel with the first solenoid valve 10.
  • the valves 10, 10b could also be other electrically actuated valves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)
EP13711447.6A 2012-03-09 2013-02-26 Hydraulic actuator and gas exchange valve arrangement Active EP2834480B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20125254A FI124349B (en) 2012-03-09 2012-03-09 Hydraulic actuator and gas exchange valve arrangement
PCT/FI2013/050213 WO2013132149A1 (en) 2012-03-09 2013-02-26 Hydraulic actuator and gas exchange valve arrangement

Publications (2)

Publication Number Publication Date
EP2834480A1 EP2834480A1 (en) 2015-02-11
EP2834480B1 true EP2834480B1 (en) 2016-02-24

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ID=47915285

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13711447.6A Active EP2834480B1 (en) 2012-03-09 2013-02-26 Hydraulic actuator and gas exchange valve arrangement

Country Status (5)

Country Link
EP (1) EP2834480B1 (ko)
KR (1) KR102032010B1 (ko)
CN (1) CN104160119B (ko)
FI (1) FI124349B (ko)
WO (1) WO2013132149A1 (ko)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109027322B (zh) * 2018-09-24 2019-07-02 中煤科工集团重庆研究院有限公司 二位四通阀

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3209737A (en) * 1962-06-27 1965-10-05 Mitsubishi Shipbuilding & Eng Valve operating device for internal combustion engine
DE2008668C3 (de) * 1970-02-25 1980-08-21 Robert Bosch Gmbh, 7000 Stuttgart Vorrichtung zum Steuern eines Einlaß- oder Auslaßventils einer Brennkraftmaschine
JPS5639953A (en) * 1979-09-04 1981-04-15 Aisin Seiki Co Ltd Oil hydraulic servo unit
JPS641652A (en) * 1987-06-24 1989-01-06 Sumitomo Electric Ind Ltd Liquid pressure booster
JPH0834343A (ja) * 1994-07-21 1996-02-06 Sumitomo Electric Ind Ltd 液圧ブースタ
JP2002138807A (ja) * 2000-11-07 2002-05-17 Nippon Soken Inc 内燃機関の動弁装置
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
JP4686561B2 (ja) * 2008-02-14 2011-05-25 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド 大型２サイクルディーゼルエンジン用の排気弁アクチュエータ
FI124120B (fi) * 2008-07-31 2014-03-31 Wärtsilä Finland Oy Ohjausjärjestely mäntämoottorissa
FI20095970L (fi) * 2009-09-21 2011-03-30 Waertsilae Finland Oy Järjestely kaasunvaihtoventtiilin käyttämiseksi

Also Published As

Publication number Publication date
WO2013132149A1 (en) 2013-09-12
CN104160119A (zh) 2014-11-19
FI20125254A (fi) 2013-09-10
FI124349B (en) 2014-07-15
CN104160119B (zh) 2016-08-31
EP2834480A1 (en) 2015-02-11
KR102032010B1 (ko) 2019-10-14
KR20140140571A (ko) 2014-12-09

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