CN102414402B - Control arrangement for inlet valve in piston engine - Google Patents
Control arrangement for inlet valve in piston engine Download PDFInfo
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- CN102414402B CN102414402B CN201080018262.0A CN201080018262A CN102414402B CN 102414402 B CN102414402 B CN 102414402B CN 201080018262 A CN201080018262 A CN 201080018262A CN 102414402 B CN102414402 B CN 102414402B
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- room
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Classifications
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/146—Push-rods
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
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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
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/245—Hydraulic tappets
- F01L1/255—Hydraulic tappets between cam and rocker arm
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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
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/16—Silencing impact; Reducing wear
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
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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
- F01L2305/00—Valve arrangements comprising rollers
Abstract
The invention relates to a control arrangement for an inlet valve in a piston engine adapted between a cam device (5) of a camshaft (4) of the engine (1) and an inlet valve mechanism (6) arranged to open and close the inlet valve (3) in association with a cylinder of the engine, which control arrangement (7) comprises a body part (8), in which a piston device (9) is movably arranged to be in force transmission connection with the camshaft (4) and the valve mechanism (6), said body part (8) and the piston device (9) together defining a first chamber (13), into which hydraulic medium can be selectively fed, and a second chamber (19) connected to the first chamber via duct means (18,18', 18"), the flow of hydraulic medium from the first chamber (13) to the second chamber (19) being controlled for providing a delay in the closing of the inlet valve (3). The body p a r t ( 8 ) i s provided with two or more flow ducts (18a,18b,18c; 18'a,18'b; 18"a,18"b,18"c) for arranging different routes for the flow of hydraulic medium from the first chamber (13) to the second chamber (19). Control means (17, 17', 17") are provided for selecting the route of flow to be utilised in each case to provide different closing delay.
Description
Technical field
The present invention relates to a kind of control apparatus of the suction valve for reciprocating engine.
Background technique
In the running of quartastroke engine, have such situation, that is, during compression stroke, cylinder does not have enough air that self ignition occurs.For high-pressure aerated motor (such as two-stage turbine supercharged engine), especially true during engine start and load variations.In this motor, utilized the higher pressure combining with sharper keen or shorter cam nose form, correspondingly caused inflation action to occur in the short period of time.Therefore,, for this special case, the opening time of suction valve under the standard load of motor falls short of.
On the other hand, minimum in order to make from the discharge of diesel engine, the timing of suction valve need to make suction valve before the lower dead centre of piston by closure early, meanwhile, boost pressure correspondingly raises, to obtain the enough air for cylinder.Yet for the boost pressure of turbosupercharger still relatively low low engine load, this device is problematic.
A solution is, under this special case, in the opening stage of suction valve, to strengthen the supply of air inlet.Another kind of solution is, when needed, and for the closure of suction valve provides delay, to extend the opening time of suction valve.In patent announcement WO2008/000899, disclose a solution for this variable intake valve closed (VIC), thought that the closure of suction valve provides certain delay.
An object of the present invention is to provide the further improved control apparatus for the closure of the suction valve of reciprocating engine is postponed of a kind of quilt.Specific purposes are to make it possible to select different retard time to meet different situations, especially when combustion engine is while turning round under low engine load and during engine start.
Summary of the invention
Object of the present invention can be substantially as a first aspect of the present invention and present and disclosedly in the other side of more details of different mode of executions of the present invention meet.According to a first aspect of the invention, main part is provided with two or more flow duct, thinks the different route of flow arrangement of the hydraulic medium that flows to the second Room from the first Room.In addition, be provided with control gear, with the glide path of selecting to treat to use in each case, to provide different closures to postpone.Route can comprise according to the application in every kind of situation one or more flow duct herein.Thus, can obtain a kind of easy to implement, the reliable and solution that can use as required.
Described two or more flow duct are advantageously arranged to be opened in common chamber or similar connecting tube, and the chamber that this is common or similar connecting tube are arranged to be communicated with described the first Room.So described control gear is arranged to operate in described common chamber or similar connecting tube.
In practice, advantageously, described the second Room is arranged in guide member, and this guide member is disposed between cam gear and piston apparatus, moving in response to the motion of described cam gear.Thus, described two or more flow duct are arranged to lead to described the second Room at the diverse location place of the movement locus along described guide member.This provides a kind of reliable structure.In addition, described guide member is arranged to: when utilizing delay feature, only along the direction of opening described suction valve, directly act on described piston apparatus.
According to a mode of execution, the mobile of described hydraulic medium is arranged to once by flow duct described in one of them, and described control gear comprises the control valve with movable valve member, described movable valve member setting needs to be disposed in the releasing device of the position of flow duct described in one of them.Described releasing device can be narrow, and the size of this narrow is determined to be and once only allows to flow through a pipeline.
According to another mode of execution, described control apparatus comprises that independent control valve for each of described flow duct is to provide the retard time of shortening.
The control system that described control gear is advantageously arranged to be included in described motor by utilization pneumatically operates.Particularly, the inflation air from the turbosupercharger of described reciprocating engine can be used to control described control gear.Operation pressure is advantageously arranged to the power of antagonistic spring and occurs, thereby simple structure and control are provided.
Accompanying drawing explanation
With reference to schematic accompanying drawing, only by embodiment, the present invention is described hereinafter, in accompanying drawing:
Fig. 1 shows the skeleton diagram of reciprocating engine and valve system thereof;
Fig. 2 to Fig. 4 shows according to the synoptic diagram of the control apparatus in the independent continuous operation stage of the present invention;
Fig. 5 shows according to the enlarged view of the first mode of execution of control gear of the present invention;
Fig. 6 a and Fig. 6 b show according to the enlarged view of the second mode of execution of the control gear in two different operating positions of the present invention;
Fig. 7 shows the relative opening curves about the suction valve of the mode of execution of Fig. 6 a; And
Fig. 8 shows according to the enlarged view of the 3rd mode of execution of control gear of the present invention.
Embodiment
Fig. 1 shows the schematic diagram of the reciprocating engine relevant with the understanding of the present invention 1.The gas exchange of the cylinder (not shown) in reciprocating engine 1 is to carry out under the control that is positioned at the gas exchange valve (that is, suction valve and outlet valve) in cylinder head 2.Only show suction valve 3, and these suction valves are by means of conventionally being operated by the valve system 6 that is arranged in the cam profile 5 ' guiding of the cam gear 5 on the camshaft 4 of motor.Each valve system 6 connects and is realized by control apparatus 7 with power transmission between corresponding cam gear 5.
In Fig. 2 to Fig. 4, illustrate in greater detail control apparatus 7, Fig. 2 wherein illustrates this control apparatus in off position, and coupled suction valve 3 is closed thus.Control apparatus 7 comprises the main part 8 that is conventionally attached to engine main body.In main part 8, be movably furnished with piston apparatus 9.The upper end of piston apparatus 9 is arranged to be connected with valve system 6 power transmission.This connection is mechanical in this case, but it can be also hydraulic pressure.The motion of piston apparatus 9 is controlled by the guide member 10 that is arranged in the lower end of the piston apparatus in main part 8.Guide member 10 engages with spring 11, and is promoted towards roller 12 by this spring 11, and described roller receives it from the guiding of the cam profile 5 ' of cam gear 5.Therefore, when camshaft 4 rotates, in Fig. 2 to Fig. 4, along in the direction of the clock, roller 12 is followed the cam profile 5 ' of cam gear 5, and the variation in cam profile 5 ' is passed, to affect the open and close of suction valve 3.
Therefore,, in Fig. 2, control apparatus 7 is in off position, and roller 12 is positioned on the basic circle of cam profile 5 '.In Fig. 3, cam gear 5 is turned clockwise, so that in the figure, the protuberance in cam profile 5 ' upwards promotes roller 12.Therefore, guide member 10 and piston apparatus 9 also move up, result, corresponding suction valve 3(is not shown) be opened.Meanwhile, the first Room 13 is filled with by the hydraulic medium of feeding pipeline 14 feedings.
In Fig. 4, roller 12 has been got back on the basic circle of cam profile 5 '.Due to the hydraulic medium in the first Room 13, first piston apparatus 9 remains in its tip position, thereby also keeps INO.As seen in Fig. 4, the joint between piston apparatus 9 and guide member 10 is disconnected thus.After this, when the hole of guide member 10 10a moves to the position of opening of pipeline 18, the pressure in the first Room 13 is released, and in the figure, piston apparatus 9 starts to move down, thereby also allows suction valve closed.So, also re-established the contact between piston apparatus 9 and guide member 10.Hydraulic medium further 19 flows to and provides lubricated oil groove for camshaft and coupled parts from chamber.
In the situation that do not use closed (VIC) function of the variable intake valve relevant with chamber 13, piston apparatus 9 is connected continuously with guide member 10, and the connection between 13He chamber, chamber 19 is set up in a conventional manner.
Fig. 5 shows the first mode of execution according to control apparatus 17 of the present invention.Chamber 16 is provided with three pipeline 18a, 18b and 18c, these three ducted each all can be arranged to be communicated with via 10aYu chamber, hole 19 by means of control apparatus 17, described control apparatus comprises and can be arranged in the mobile control valve 17a in chamber 20 of main part 8.Control valve 17a is provided with valve member 17b and releasing device 17c, and this releasing device 17c is the groove around valve member 17b in this case.In Fig. 5, releasing device 17c is positioned at the position of pipeline 18b, and thus, the connection between chamber 13 and 19 is set up by this pipeline 18b.As obviously found out from scheming, pipeline 18a, 18b and 18c's is open-ended in different height.This means, between the moving period of guide member 10, the open-ended position that is positioned to hole 10a the time different of these pipelines, thus, in chamber 13, the release of pressure will occur in the different time respectively.Therefore, this provides different delays with regard to needs according to selected pipeline in each case and for the closure of suction valve.
The operation of control valve unit 17 can be advantageously by being pneumatically fed into pressure air in chamber 20 and realizing, and as shown by arrow, this will cause the power of antagonistic spring 21 and the control valve 17a with valve member 17b is pushed to the left side in figure.Therefore, the motion of control valve 17a and the pressure that the selection of corresponding pipeline 18a, 18b and 18c depended on to the air in chamber 20 to be fed to.Preferably, the control system of motor should be used as making can example Tathagata from the inflation air of the turbosupercharger of motor.Thus, can carry out automatically to realize more or less the variation in suction valve closure according to the inflation air pressure that depends on the load of every kind of motor in situation.
Fig. 6 a and Fig. 6 b disclose another mode of execution of control gear 17 '.In this case, the chamber 16 ' that forms connecting tube is operably connected with control valve 17 ' a, control member 17 ' the b control room 16 ' of control valve and the connection between second pipe 18 ' b.Control valve 17 ' a is arranged in chamber 20 ', and pressure air is fed in chamber 20 ', with the power of antagonistic spring 21 ', promotes control valve.As shown in Figure 6 b, when the connection between chamber 16 ' and pipeline 18 ' b is closed, the connection between chamber 13 and 19 is set up via pipeline 18 ' a.On the other hand, as shown in Figure 6 a, when the connection between chamber 16 ' and pipeline 18 ' b is opened, the connection between chamber 13 and 19 is set up via pipeline 18 ' b earlier, open-ended higher than pipeline 18 ' a of this pipeline 18 ' b open-ended.Yet also in this case, pipeline 18 ' a stays open, and do not need to there is the independent control valve for closed duct 18 ' a.
Figure 7 illustrates operation and the effect to the closed delay of the suction valve of motor thereof of the mode of execution of Fig. 6 a and Fig. 6 b, this Fig. 7 shows the relative opening curves of function of the cam angle as motor of suction valve.Curve C shows a kind of like this situation, and in this case, hydraulic medium is not directed in chamber 13 completely, and thus, the control of suction valve is only carried out like that by cam profile 5 ' is determined.Curve A and curve B relate to that hydraulic medium is directed in chamber 13 and piston apparatus 9 in the situation that direction moves of opening of suction valve.Therefore, can be with respect to the normal operation of suction valve, for example, in the different load situation of motor, for the closure of suction valve provides delay.Curve A relates to a kind of like this situation, and in this case, when affecting delay by connection between selecting via the chamber 13 and 19 of pipeline 18 ' a, control valve 17 ' a is the position in closed duct 18 ' b therefore, as shown in Figure 6 b.And curve B has represented the situation corresponding to Fig. 6 a, according to this curve B, control valve 17 ' a opens, and allows to be communicated with via pipeline 18 ' b.Thus, the release of the pressure in chamber 13 occurs earlier, and suction valve is therefore also closed earlier, but compares with the conventional situation being represented by curve A, and closure is still delayed.
Fig. 8 discloses the 3rd mode of execution according to control gear of the present invention.This is the modification of the mode of execution of Fig. 6 a and Fig. 6 b, except pipeline 18 ' ' a and 18 ' ' b, this control gear also comprises the 3rd pipeline 18 ' ' c.As can be seen, these ducted each open-ended are positioned at different height, that is to say, be positioned at diverse location, thereby the possibility that changes the closed delay of suction valve is provided along the return movement of guide member 10.In principle, according to the free space in main part 8 in the needs of the more approaching modification of the available delay of closure of the suction valve of discussing in every kind of situation and motor, the pipeline 18 ' of greater number can also be set respectively '.
In the situation that the mode of execution of Fig. 6 a, Fig. 6 b and Fig. 8, control valve 17,17 ' and 17 ' ' can operate by means of any pressure medium, available any pressure medium in motor preferably, that is, air pressure, hydraulic pressure or also have electric power.In each case, to the selection of the control of control valve and flow pipeline, can be used for the pressure transducer of each control valve and the control logic of expection arranges by utilization, to determine needed delay in every kind of situation, and correspondingly guarantee the proper operation of control valve.
The present invention is not limited to the above embodiment, but can in the scope of design of the present invention and claims, with multiple other different mode of execution, implement.
Claims (9)
1. the control apparatus for the suction valve of reciprocating engine, this control apparatus is suitable for being positioned between the cam gear (5) and suction valve mechanism (6) of camshaft (4) of described motor (1), this suction valve mechanism is arranged to and the cylinder of described motor open and close suction valve (3) explicitly, described control apparatus (7) comprises main part (8), in this main part, piston apparatus (9) is arranged to that power transmission is connected with described valve system (6) with described camshaft (4) movably, described main part (8) and described piston apparatus (9) limit the first Room (13) and the second Room (19) together, hydraulic medium can be optionally fed in described the first Room, described the second Room is via tube equipment (18, 18 ', 18 ' ') be connected to described the first Room, mobile be controlled of described hydraulic medium from described the first Room (13) to described the second Room (19) thinks that the closure of described suction valve (3) provides delay, described control apparatus is characterised in that, described main part (8) is provided with two or more flow duct (18a, 18b, 18c, 18 ' a, 18 ' b, 18 ' ' a, 18 ' ' b, 18 ' ' c), think the different route of flow arrangement that flows to the hydraulic medium of described the second Room (19) from described the first Room (13), and be provided with control gear (17,17 ', 17 ' '), with selection, treat the glide path of using in each case, to provide different closures to postpone
Described the second Room (19) is arranged in guide member (10), this guide member is disposed between described cam gear (5) and described piston apparatus (9), moving in response to the motion of described cam gear (5), and, described two or more flow duct (18a, 18b, 18c; 18 ' a, 18 ' b; 18 ' ' a, 18 ' ' b, 18 ' ' c) be arranged to lead to described the second Room (19) at the diverse location place of the movement locus along described guide member (10).
2. control apparatus according to claim 1, is characterized in that, described two or more flow duct (18a, 18b, 18c; 18 ' a, 18 ' b; 18 ' ' a, 18 ' ' b, 18 ' ' c) be arranged in common chamber (16,16 ', 16 ' ') or in similar connecting tube open, the chamber that this is common or similar connecting tube are arranged to described the first Room (13) and are communicated with, and, described control gear (17,17 ', 17 ' ') be arranged to operate in described common chamber (16,16 ', 16 ' ') or similar connecting tube.
3. control apparatus according to claim 1, is characterized in that, described guide member (10) is arranged to only along acting directly on described piston apparatus (9) for opening the direction of described suction valve (3).
4. according to control apparatus in any one of the preceding claims wherein, it is characterized in that, the mobile of described hydraulic medium is arranged to once by flow duct (18a described in one of them, 18b, 18c), and described control gear (17) comprises the control valve (17a) with movable valve member (17b), and described valve member (17b) setting needs to be disposed in flow duct (18a described in one of them, 18b, 18c) the releasing device (17c) of position.
5. control apparatus according to claim 4, is characterized in that, described releasing device (17c) is narrow, and the size of this narrow is confirmed as once only allowing to flow through a pipeline (18a, 18b, 18c).
6. according to the control apparatus described in any one in claims 1 to 3, it is characterized in that, described control apparatus comprises for described flow duct (18 ' b; The independent control valve of each 18 ' ' b, 18 ' ' c) (17 ' a, 17 ' ' a), to be provided the retard time of shortening.
7. according to the control apparatus described in any one in claims 1 to 3, it is characterized in that, the control system that described control gear (17,17 ', 17 ' ') is arranged to be included in described motor by utilization pneumatically operates.
8. control apparatus according to claim 7, is characterized in that, from the inflation air of the turbosupercharger of described reciprocating engine, is arranged to for controlling described control gear (17,17 ', 17 ' ').
9. control apparatus according to claim 7, is characterized in that, the power that described control gear (17,17 ', 17 ' ') is arranged to be included in by utilization the control system antagonistic spring in described motor pneumatically operates.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FI20095462 | 2009-04-27 | ||
| FI20095462A FI121512B (en) | 2009-04-27 | 2009-04-27 | Control arrangement for a suction valve in a piston engine |
| PCT/FI2010/050285 WO2010125235A1 (en) | 2009-04-27 | 2010-04-09 | A control arrangement for an inlet valve in a piston engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102414402A CN102414402A (en) | 2012-04-11 |
| CN102414402B true CN102414402B (en) | 2014-03-12 |
Family
ID=40590341
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080018262.0A Active CN102414402B (en) | 2009-04-27 | 2010-04-09 | Control arrangement for inlet valve in piston engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2425104B1 (en) |
| KR (1) | KR101628424B1 (en) |
| CN (1) | CN102414402B (en) |
| FI (1) | FI121512B (en) |
| WO (1) | WO2010125235A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101623222B1 (en) | 2011-05-16 | 2016-05-23 | 현대중공업 주식회사 | Variable valve timing system using hydraulic system |
| FI124576B (en) * | 2012-10-18 | 2014-10-31 | Wärtsilä Finland Oy | Gasväxelventilarrangemang |
| KR101371827B1 (en) * | 2012-10-19 | 2014-03-07 | 현대중공업 주식회사 | Variable valve timing apparatus |
| DE202012012656U1 (en) * | 2012-11-12 | 2013-08-05 | Schaeffler Technologies AG & Co. KG | Pump unit with rolling tap |
| FI20135003L (en) * | 2013-01-03 | 2014-07-04 | Waertsilae Finland Oy | Drain valve device and method for checking closure of a drain valve |
| CN104443595B (en) * | 2014-11-26 | 2016-08-24 | 李淑兰 | A kind of air valve structure of improvement |
| DK179120B1 (en) * | 2016-02-03 | 2017-11-13 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A large turbocharged two-stroke compression-ignited internal combustion engine with blow-off control |
| AT518408B1 (en) * | 2016-04-05 | 2017-10-15 | Avl List Gmbh | VALVE CONTROL DEVICE FOR AT LEAST ONE GAS CHANGING VALVE |
| EP3596317B1 (en) * | 2017-03-17 | 2023-05-03 | Wärtsilä Finland Oy | A control arrangement for a gas exchange valve in an internal combustion piston engine and method of operating a control arrangement for a gas exchange valve in an internal combustion engine |
| GB201815263D0 (en) * | 2018-09-19 | 2018-10-31 | Eaton Intelligent Power Ltd | Valve train assembly |
| EP3715594B1 (en) * | 2019-03-29 | 2021-10-27 | ABB Schweiz AG | Valve drive with hydraulic delay element for a combustion engine |
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| DE3611476A1 (en) * | 1986-04-05 | 1987-10-08 | Irm Antriebstech Gmbh | Method for the actuation of valves for exhaust and refill in internal combustion engines with direct hydraulic transmission |
| US5002022A (en) * | 1989-08-30 | 1991-03-26 | Cummins Engine Company, Inc. | Valve control system with a variable timing hydraulic link |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1399813A (en) * | 1971-10-25 | 1975-07-02 | Innovation Technical Dev Co Lt | Motion transmitting unit for use in varying the reciprocating movement of a member |
| DE3807699A1 (en) * | 1988-03-09 | 1989-09-21 | Audi Ag | Adjustable hydraulic valve timing gear |
| US6883477B2 (en) * | 2002-10-07 | 2005-04-26 | Ricardo, Inc. | Apparatus for deactivating an engine valve |
| FI124107B (en) * | 2006-06-30 | 2014-03-14 | Wärtsilä Finland Oy | Piston Engine Gas Exchange Valve Control Arrangement and Method for Controlling a Piston Engine Gas Exchange Valve |
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2009
- 2009-04-27 FI FI20095462A patent/FI121512B/en active
-
2010
- 2010-04-09 KR KR1020117025211A patent/KR101628424B1/en active IP Right Grant
- 2010-04-09 EP EP10718624.9A patent/EP2425104B1/en active Active
- 2010-04-09 CN CN201080018262.0A patent/CN102414402B/en active Active
- 2010-04-09 WO PCT/FI2010/050285 patent/WO2010125235A1/en active Application Filing
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3611476A1 (en) * | 1986-04-05 | 1987-10-08 | Irm Antriebstech Gmbh | Method for the actuation of valves for exhaust and refill in internal combustion engines with direct hydraulic transmission |
| US5002022A (en) * | 1989-08-30 | 1991-03-26 | Cummins Engine Company, Inc. | Valve control system with a variable timing hydraulic link |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2425104B1 (en) | 2014-04-09 |
| CN102414402A (en) | 2012-04-11 |
| FI20095462A (en) | 2010-10-28 |
| WO2010125235A1 (en) | 2010-11-04 |
| KR101628424B1 (en) | 2016-06-08 |
| FI121512B (en) | 2010-12-15 |
| EP2425104A1 (en) | 2012-03-07 |
| KR20120016068A (en) | 2012-02-22 |
| FI20095462A0 (en) | 2009-04-27 |
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