EP2834480B1 - Hydraulic actuator and gas exchange valve arrangement - Google Patents
Hydraulic actuator and gas exchange valve arrangement Download PDFInfo
- 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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- European Patent Office
- Prior art keywords
- valve
- pressurizing chamber
- actuator
- drive piston
- input portion
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- 239000012530 fluid Substances 0.000 claims description 50
- 238000004891 communication Methods 0.000 claims description 11
- 238000002485 combustion reaction Methods 0.000 claims description 6
- 239000007787 solid Substances 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000005553 drilling Methods 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
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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
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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Actuator (AREA)
Description
- 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. - 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. These kinds of arrangements are reliable, but also inflexible. Valve timing is difficult to adjust and if variable valve closing or opening timing is needed, valve mechanisms become complicated. In an electro-hydraulic systems valve timing can be changed easily. However, the flexibility is often achieved at the cost of reduced reliability.
- 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 according to the invention 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 according to the invention 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.
- With the hydraulic actuator and the gas exchange valve arrangement according to the invention, 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.
- According to an embodiment of the invention, the actuator comprises a control valve for actuating the hydraulic valve.
- According to another embodiment of the invention, 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.
- According to another embodiment of the invention, 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.
- According to another embodiment of the invention, 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. When the flow into and out of the input portion of the pressurizing chamber is limited, smooth acceleration and deceleration of the drive piston is ensured. 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.
- According to another embodiment of the invention, the inlet duct and the outlet duct are provided with adjustable throttles for regulating flow rates in the ducts. With adjustable throttles, gas exchange valve opening and closing speeds can be changed.
- According to another embodiment of the invention, 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. With the second drive piston, the needed hydraulic pressure is lower and energy can be saved.
- According to another embodiment of the invention, 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.
- According to an embodiment of the invention, 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.
- According to an embodiment of the invention, 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.
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Fig. 1 shows a gas exchange valve arrangement according to an embodiment of the invention. -
Fig. 2 shows the arrangement ofFig. 1 with open gas exchange valves. -
Fig. 3 shows a gas exchange valve arrangement according to a second embodiment of the invention. -
Fig. 4 shows a gas exchange valve arrangement according to a third embodiment of the invention. -
Fig. 5 shows a gas exchange valve arrangement according to a fourth embodiment of the invention. -
Fig. 6 shows a gas exchange valve arrangement according to a fifth embodiment of the invention. -
Fig. 7 shows part of a valve actuator according to an embodiment of the invention. - Embodiments of the invention are now described in more detail with reference to the accompanying drawings.
- 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 agas exchange duct 2 and a cylinder of the engine. Thegas exchange valves 1, 1' can be either intake valves or exhaust valves, and thegas exchange duct 2 is thus either an intake duct or an exhaust duct. In the embodiments shown in the accompanying figures, the arrangement comprises a firstgas exchange valve 1 and a second gas exchange valve 1'. In an engine, in which the arrangement is used, each cylinder of the engine is provided with a gas exchange valve arrangement according to the invention. Preferably, there is a similar arrangement for both the intake valves and the exhaust valves. Thegas exchange valves 1, 1' are arranged in thecylinder head 4 of the respective cylinder. Eachgas 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 acorresponding valve seat 1d, Id'. Avalve spring 16, 16' is arranged around the valve stem 1b, 1b' of eachgas exchange valve 1, 1' for closing thegas exchange valve 1, 1'. Thecylinder head 4 is provided withvalve guides 17, 17' for accommodating thegas exchange valves 1, 1'. - The
gas exchange valves 1, 1' are electro-hydraulically operated. For operating thegas exchange valves 1, 1', each gas exchange valve arrangement comprises ahydraulic actuator 35. Thehydraulic actuator 35 comprises a pressurizingchamber 9, in which adrive piston 7 is arranged. Thedrive piston 7 divides the pressurizingchamber 9 into at least oneinput portion 9a and at least oneoutput portion 9b. In the embodiment of the figures, the pressurizingchamber 9 is divided into oneinput portion 9a and into a first and asecond output portion drive piston 7 can reciprocate in the pressurizingchamber 9. When pressure medium is introduced into theinput portion 9a of the pressurizingchamber 9, thedrive piston 7 pressurizes hydraulic fluid on theoutput side chamber 9. A returningspring 18 is arranged in the pressurizingchamber 9 for pushing thedrive piston 7 towards theinput portion 9a of the pressurizingchamber 9. However, the return stroke of thedrive piston 7 could also be implemented by introducing hydraulic fluid into theoutput portion 9b of the pressurizingchamber 9. Thehydraulic actuator 35 comprises ahydraulic valve 10 for opening and closing flow communication between a pressure source, such as ahydraulic pump 12, and theinput portion 9a of the pressurizingchamber 9. Thehydraulic valve 10 also prevents and allows outflow from theinput portion 9a of the pressurizingchamber 9. Thehydraulic valve 10 is arranged between ahydraulic pump 12 and theinput portion 9a of the pressurizingchamber 9. In a first position of thehydraulic valve 10, flow from aninlet duct 15 into theinput portion 9a of the pressurizingchamber 9 is allowed and flow from theinput portion 9a into anoutlet duct 21 is prevented, as shown infigure 2 . In a second position of thehydraulic valve 10, flow from theinlet duct 15 into theinput portion 9a of the pressurizingchamber 9 is prevented and flow from theinput portion 9a into theoutlet duct 21 is allowed, as shown infigure 1 . The samehydraulic valve 10 is thus used for controlling valve opening and closing timing of bothgas exchange valves 1, 1'. Thehydraulic actuator 35 further comprisesfluid outlets output portions chamber 9 to thegas exchange valves 1, 1'. - A driven
piston gas exchange valve 1, 1'. Thegas exchange valve 1, 1' is thus moved together with the drivenpiston piston chamber 5, 5' that is in fluid communication with theoutput portion chamber 9. Thefirst output portion 9b of the pressurizingchamber 9 is connected with a first connectingduct 6 to the receivingchamber 5 of the firstgas exchange valve 1, and thesecond output portion 9b' of the pressurizingchamber 9 is connected with a second connecting duct 6' to the receiving chamber 5' of the second gas exchange valve 1'. Since thehydraulic actuator 35 is provided with anown output portion gas exchange valves 1, 1', the pressurized hydraulic fluid is supplied simultaneously to both of thegas exchange valves 1, 1'. - When hydraulic fluid is introduced into the
input portion 9a of the pressurizingchamber 9, thedrive piston 7 moves and pressurizes hydraulic fluid in theoutput portions chamber 9. From theoutput portions chamber 9, the hydraulic fluid flows into the receivingchambers 5, 5' and thegas exchange valves 1, 1' are opened. When hydraulic fluid is released from theinput portion 9a of the pressurizingchamber 9, thedrive piston 7 can be moved backwards by the returningspring 18. Hydraulic fluid can thus flow from the receivingchambers 5, 5' back into theoutput portions chamber 9 and thegas exchange valves 1, 1' can be closed by the valve springs 16, 16'. - In the embodiment of
figures 1 and 2 , anintermediate duct 20 is arranged between thehydraulic valve 10 and the pressurizingchamber 9 for connecting theinput portion 9a of the pressurizingchamber 9 to thehydraulic valve 10. Thehydraulic valve 10 is a hydraulically actuated slide valve. Thehydraulic valve 10 is a three-way valve that comprises afirst port 10a that is connected to theinlet duct 15, asecond port 10b that is connected to theoutlet duct 21, and athird port 10c that is connected to theintermediate duct 20. Thehydraulic valve 10 comprises aspindle 22 that has a first position and a second position. In the first position of thespindle 22, flow communication between thefirst port 10a and thethird port 10c is closed and flow communication between thesecond port 10b and thethird port 10c is open. Hydraulic fluid can thus flow from theinlet duct 15 into theintermediate duct 20, but flow from theintermediate duct 20 into theoutlet duct 21 is prevented. In the second position of thespindle 22, flow communication between thefirst port 10a and thethird port 10c is open and the flow communication between thesecond port 10b and thethird port 10c is closed. Hydraulic fluid can thus flow from theintermediate duct 20 into theoutlet duct 21, but flow from theinlet duct 15 into theintermediate duct 20 is prevented. Thehydraulic valve 10 is provided with aspring 19 that keeps thespindle 22 in the first position when thehydraulic valve 10 is not actuated. When an external force is applied to thespindle 22, thespindle 22 is moved to the second position. For applying the force on thespindle 22, thehydraulic actuator 35 is provided with acontrol valve 11. Thecontrol valve 11 is a hydraulic valve that is operated with a solenoid. Thecontrol valve 11 could also be some other kind of electrically actuated valve. When thecontrol valve 11 is in the position offigure 2 , hydraulic fluid is introduced onto a pressure surface 23 of thespindle 22 for moving thespindle 22. In the embodiment offigures 1 and 2 , the receivingchamber 5, 5' is arranged around the valve stem 1b, 1b' and the drivenpiston cylinder head 4. - The output portion end of the
drive piston 7 is formed a solidcylindrical part 7b and the input portion end of thedrive piston 7 is formed of a hollowcylindrical part 7a. The input portion end of thesolid cylinder 7b forms a surface onto which the pressure of the hydraulic fluid is applied. The hydraulic fluid is introduced into theinput portion 9a of the pressurizingchamber 9 through the sleeve of thehollow cylinder 7a. The sleeve is therefore provided with at least one opening, which consists of agroove 13a and adrilling 13b. In the embodiment of the figures, twodrillings 13b are in connection with thegroove 13a. Because of thegroove 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 thedrive piston 7. Thegroove 13a widens towards the outer surface of the hollow cylinder and is only partially aligned with theintermediate duct 20 when thedrive piston 7 is at the input portion end of the pressurizingchamber 9. Therefore, the flow into theinput portion 9a of the pressurizingchamber 9 is throttled when thehydraulic valve 10 is moved into the second position and fluid supply from thehydraulic pump 12 into the pressurizingchamber 9 is allowed. Consequently, thedrive piston 7 accelerates smoothly. When thedrive piston 7 moves forward, thegroove 13a becomes fully aligned with theintermediate duct 20 and maximum flow into theinput portion 9a of the pressurizingchamber 9 is allowed. When thedrive piston 7 approaches the output portion end of the pressurizingchamber 9, thegroove 13a becomes again partly overlapping with the walls of the pressurizingchamber 9. The flow into theinput portion 9a of the pressurizingchamber 9 is thus limited and thedrive piston 7 slows down. The movement of thedrive piston 7 in the opposite direction works in a similar way. Since the outflow from theinput portion 9a of the pressurizingchamber 9 is throttled at the beginning and at the end of the movement of thedrive piston 7, both the acceleration and deceleration of thedrive piston 7 is smooth. - There are also other ways for achieving the throttling effect. In
figure 7 is shown part of avalve actuator 35, where the opening of the drive piston is astraight drilling 13b. Theintermediate duct 20 between thehydraulic valve 10 and theinput portion 9a of the pressurizingchamber 9 is connected to agroove 13c that encircles the inner surface of the pressurizingchamber 9. When thedrive piston 7 is at the output portion end of the pressurizingchamber 9, as shown infigure 7 , or at the input portion end of the pressurizingchamber 9, thedrilling 13b of thedrive piston 7 is only partially aligned with thegroove 13c of theinput portion 9a of the pressurizingchamber 9. The flow out of theinput portion 9a of the pressurizingchamber 9 or into it is thus throttled. Thegroove 13c is chamfered so that the flow area is very small at the beginning and at the end of the movement of thedrive piston 7. - The
drive piston 7 further comprises a boring 39, which connects theinput portion 9a of the pressurizingchamber 9 to theoutput portion 9b. Asecond boring 40 connects theinput portion 9a to thesecond output portion 9b'. Through theborings valve actuator 35 can be compensated. The diameters of theborings borings hydraulic actuator 35. Theinput portion 9a and theoutput portions chamber 9 are also provided withair removal ports air removal ports air removal ports throttles figure 4 . - The embodiment shown in
figure 3 differs from the embodiment offigures 1 and 2 in terms of the construction of thehydraulic valve 10. Thehydraulic valve 10 offigure 3 comprises afourth port 10d. Thehydraulic actuator 35 comprises a firstintermediate duct 20 and a secondintermediate duct 28. Thefirst port 10a of thehydraulic valve 10 is connected to theinlet duct 15 and thethird port 10c is connected to the firstintermediate duct 20. Thesecond port 10b is connected to theoutlet duct 21 and thefourth port 10d is connected to the secondintermediate duct 28. In the first position of thehydraulic valve 10, thespindle 22 allows flow from theinlet duct 15 into the firstintermediate duct 20 and prevents flow from the secondintermediate duct 28 into theoutlet duct 21. In the second position of thehydraulic valve 10, thespindle 22 allows flow from the secondintermediate duct 28 into theoutlet duct 21 and prevents flow from theinlet duct 15 into the secondintermediate duct 28. Hydraulic fluid is introduced into theinput portion 9a of the pressurizingchamber 9 through the firstintermediate duct 20. The hydraulic fluid is released from theinput portion 9a of the pressurizingchamber 9 through the secondintermediate duct 28. In the embodiment offigure 3 , separate fluid supply to thecontrol valve 11 is not needed. Theinlet duct 15 is connected with acontrol duct 26 to afluid chamber 27 that is arranged at one end of thespindle 22. Together with thespring 19 of thehydraulic valve 10, the pressure in thefluid chamber 27 keeps thehydraulic valve 10 in the first position, when thecontrol valve 11 is closed. When thecontrol valve 11 is opened, hydraulic fluid is released from thefluid chamber 27 and thehydraulic valve 10 is switched into the second position. In the embodiment offigure 3 , the drivenpiston - In the embodiment of
figure 4 , thehydraulic valve 10 is identical to thehydraulic valve 10 offigure 3 . In this embodiment, the first and the secondintermediate ducts intermediate duct 36 before the pressurizingchamber 9. A thirdintermediate duct 37 and a fourthintermediate duct 38 are branched from the combinedintermediate duct 36 and connected to theinput portion 9a of the pressurizingchamber 9. The diameters of the thirdintermediate duct 37 and the fourthintermediate duct 38 are smaller than the diameter of the combinedintermediate duct 36. The third and the fourthintermediate ducts check valves intermediate duct 37, flow from the combinedintermediate duct 36 into the pressurizingchamber 9 is allowed. The thirdintermediate duct 37 is located so that when thedrive piston 7 is at the input portion end of the pressurizingchamber 9, thegroove 13a of thedrive piston 7 is aligned with the end of the thirdintermediate duct 37 and direct flow from the combinedintermediate duct 36 into the pressurizingchamber 9 is prevented. Through the fourthintermediate duct 38, flow from the pressurizingchamber 9 into the combinedintermediate duct 36 is allowed. The fourthintermediate duct 38 is located so that when thedrive piston 7 is at the output portion end of the pressurizingchamber 9, theopening 13a of thedrive piston 7 is aligned with the fourthintermediate duct 38 and direct flow from the pressurizingchamber 9 into the combinedintermediate duct 36 is prevented. Flow speed is thus restricted at the beginning and at the end of the stroke of thedrive piston 7 and smooth acceleration and deceleration is achieved. In the embodiment offigure 4 , theinlet duct 15 is provided with anadjustable throttle 30. Also theoutlet duct 21 is provided with anadjustable throttle 31. With thethrottles inlet duct 15 and theoutlet duct 21 can be restricted and the opening and closing curves of thegas exchange valves 1, 1' can be affected. Smaller flow gives slower gas exchange valve opening/closing and faster flow gives quicker opening/closing. Theinput portion 9a of the pressurizingchamber 9 is provided with a second drive piston 7'. The second drive piston 7' has larger diameter and a shorter stroke than thefirst drive piston 7. Since the second drive piston 7' assists thefirst drive piston 7, smaller hydraulic pressure is needed at the beginning of the stroke of thefirst drive piston 7. Smaller hydraulic pressure decreases energy consumption of the arrangement. - The embodiment of
figure 5 differs from the embodiment offigure 4 in that the arrangement is provided with apressure accumulator 32 for energy recovery. Thepressure accumulator 32 is connected to theoutlet duct 21 upstream from thethrottle 31. Thepressure accumulator 32 is also connected to theinlet duct 15 upstream from thethrottle 30 and downstream from thehydraulic pump 12 and thepressure accumulator 32. A secondhydraulic pump 12b is arranged downstream from thehydraulic pump 12 and from the pressure accumulator 32A check valve 33 is arranged between thepressure accumulator 32 and theoutlet duct 21 for preventing flow from the firsthydraulic pump 12 or thepressure accumulator 32 into theoutlet duct 21. During the backwards stroke of thedrive piston 7, energy can be recovered from theoutlet duct 21 into thepressure accumulator 32. The firsthydraulic pump 12 supplies hydraulic fluid at a smaller pressure level than is needed for operating thedrive piston 7. The pressure of the flow from the firsthydraulic pump 12 and from thepressure accumulator 32 is raised to the sufficient level by the secondhydraulic pump 12b. - In the embodiment of
figure 6 , thehydraulic valve 10 is a solenoid valve. Since the flow capacity of a single solenoid valve is small, the arrangement is provided with asecond solenoid valve 10b that is arranged in parallel with thefirst solenoid valve 10. Thevalves - It will be appreciated by a person skilled in the art that the invention is not limited to the embodiments described above, but may vary within the scope of the appended claims. For instance, it is possible to combine features of the different embodiments.
Claims (15)
- A hydraulic actuator (35) for opening a gas exchange valve (1, 1') of an internal combustion engine, which hydraulic actuator (35) comprises- a pressurizing chamber (9) for pressurizing hydraulic fluid,- a drive piston (7) that is arranged in the pressurizing chamber (9) and which drive piston (7) divides the pressurizing chamber (9) into at least one input portion (9a) and at least one output portion (9b),- an inlet duct (15) for introducing pressurized hydraulic fluid into the input portion (9a) of the pressurizing chamber (9) for moving the drive piston (7),- a fluid outlet (9d) for supplying hydraulic fluid from the output portion (9b) of the pressurizing chamber (9) to the gas exchange valve (1, 1'), and- an outlet duct (21) for releasing hydraulic fluid from the input portion (9a) of the pressurizing chamber (9),characterized in that the actuator (35) comprises a hydraulic valve (10) having- a first position, in which position flow from the inlet duct (15) to the input portion (9a) of the pressurizing chamber (9) is allowed and flow from the input portion (9a) to the outlet duct (21) is prevented, and- a second position, in which position flow from the inlet duct (15) to the input portion (9a) of the pressurizing chamber (9) is prevented and flow from the input portion (9a) to the outlet duct (21) is allowed.
- An actuator (35) according to claim 1, characterized in that the actuator (35) comprises a control valve (11) for actuating the hydraulic valve (10).
- An actuator (35) according to claim 1 or 2, characterized in that the drive piston (7) divides the output side of the pressurizing chamber (9) into a first output portion (9b) that is provided with a first fluid outlet (9d) and into a second output portion (9b') that is provided with a second fluid outlet (9d').
- An actuator (35) according to any of claims 1-3, characterized in that the actuator (35) comprises means for throttling the flow into the input portion (9a) of the pressurizing chamber (9) and/or out of the input portion (9a) at the beginning and/or at the end of the movement of the drive piston (7).
- An actuator (35) according to any of the preceding claims, characterized in that the output portion end of the drive piston (7) is formed of a solid cylindrical part (7b) and the input portion end of the drive piston (7) is formed of a hollow cylindrical part (7a) that comprises at least one opening (13a, 13b) in the sleeve for allowing flow into and out of the input portion (9a) of the pressurizing chamber (9).
- An actuator (35) according to claim 5, characterized in that the opening (13a, 13b) comprises a groove (13a) that is arranged around the outer circumference of the hollow cylindrical part (7a) and a boring (13b) connecting the groove (13a) to the space defined by the hollow cylindrical part (7a).
- An actuator (35) according to claim 5 or 6, characterized in that the opening (13a, 13b) in the sleeve of the drive piston (7) widen towards the outer surface of the sleeve.
- An actuator (35) according to any of claims 5-7, characterized in that the opening (13a, 13b) in the sleeve of the drive piston (7) is only partially aligned with the end of an intermediate duct (20, 28) connecting the input portion (9a) of the pressurizing chamber (9) to the hydraulic valve (10) when the drive piston (7) is at the input portion end of the pressurizing chamber (9).
- An actuator (35) according to any of claims 5-8, characterized in that the opening (13a, 13b) in the sleeve of the drive piston (7) is only partially aligned with the end of an intermediate duct (20, 28) when the drive piston (7) is at the output portion end of the pressurizing chamber (9).
- An actuator (35) according to any of the preceding claims, characterized in that the inlet duct (15) and the outlet duct (21) are provided with adjustable throttles (30, 31) for regulating flow rates in the ducts (15, 21).
- An actuator (35) according to any of the preceding claims, characterized in that the actuator (35) comprises a second drive piston (7') that has a larger diameter and a shorter stroke than the first drive piston (7) and which second drive piston (7') is arranged in the input portion (9a) of the pressurizing chamber (9) for assisting the first drive piston (7) at the beginning of the pressurizing stroke.
- An actuator (35) according to any of the preceding claims, characterized in that a fluid chamber (27) that is in fluid communication with the inlet duct (15) is arranged at one end of the spindle (22) of the hydraulic valve (10), and a control valve (11) is arranged to release pressure from the fluid chamber (27) for actuating the hydraulic valve (10).
- A gas exchange valve arrangement for an internal combustion engine, which arrangement comprises- at least one gas exchange valve (1, 1') for opening and closing flow communication between a gas exchange duct (2) and a cylinder of the engine, the gas exchange valve (1, 1') comprising a valve head (1a, 1a') and a valve stem (1b, 1b'),- a receiving chamber (5, 5'), and- a driven piston (1c, 1c') that is in mechanical connection with the valve stem (1b) and arranged in the receiving chamber (5, 5'),characterized in that the arrangement comprises a hydraulic actuator (35) according to any of claims 1-12.
- An arrangement according to claim 13, characterized in that the arrangement is provided with a pressure accumulator (32) that is connected to the outlet duct (21) for recovering energy from the outlet duct (21), and to the inlet duct (15) for supplying energy into the inlet duct (15).
- An arrangement according to claim 13 or 14, characterized in that the driven piston (1c, 1c') is arranged around the valve stem (1b, 1b').
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI20125254A FI124349B (en) | 2012-03-09 | 2012-03-09 | Hydraulic actuator and throttle 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 |
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EP2834480A1 EP2834480A1 (en) | 2015-02-11 |
EP2834480B1 true EP2834480B1 (en) | 2016-02-24 |
Family
ID=47915285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP13711447.6A Active EP2834480B1 (en) | 2012-03-09 | 2013-02-26 | Hydraulic actuator and gas exchange valve arrangement |
Country Status (5)
Country | Link |
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EP (1) | EP2834480B1 (en) |
KR (1) | KR102032010B1 (en) |
CN (1) | CN104160119B (en) |
FI (1) | FI124349B (en) |
WO (1) | WO2013132149A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN109027322B (en) * | 2018-09-24 | 2019-07-02 | 中煤科工集团重庆研究院有限公司 | Two-position four-way valve |
Family Cites Families (11)
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 (en) * | 1970-02-25 | 1980-08-21 | Robert Bosch Gmbh, 7000 Stuttgart | Device for controlling an intake or exhaust valve of an internal combustion engine |
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 (en) * | 1994-07-21 | 1996-02-06 | Sumitomo Electric Ind Ltd | Hydraulic booster |
JP2002138807A (en) * | 2000-11-07 | 2002-05-17 | Nippon Soken Inc | Valve system of internal combustion engine |
JP2004084670A (en) | 2002-08-28 | 2004-03-18 | Man B & W Diesel As | Valve operated with hydraulic pressure |
US6899068B2 (en) | 2002-09-30 | 2005-05-31 | Caterpillar Inc | Hydraulic valve actuation system |
JP4686561B2 (en) | 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 | Exhaust valve actuator for large two-cycle diesel engines |
FI124120B (en) * | 2008-07-31 | 2014-03-31 | Wärtsilä Finland Oy | Steering arrangement in piston engine |
FI20095970L (en) * | 2009-09-21 | 2011-03-30 | Waertsilae Finland Oy | ARRANGEMENT FOR USING A GAS EXCHANGE VALVE |
-
2012
- 2012-03-09 FI FI20125254A patent/FI124349B/en active IP Right Grant
-
2013
- 2013-02-26 CN CN201380012490.0A patent/CN104160119B/en active Active
- 2013-02-26 EP EP13711447.6A patent/EP2834480B1/en active Active
- 2013-02-26 KR KR1020147027861A patent/KR102032010B1/en active IP Right Grant
- 2013-02-26 WO PCT/FI2013/050213 patent/WO2013132149A1/en active Application Filing
Also Published As
Publication number | Publication date |
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KR20140140571A (en) | 2014-12-09 |
EP2834480A1 (en) | 2015-02-11 |
FI124349B (en) | 2014-07-15 |
KR102032010B1 (en) | 2019-10-14 |
WO2013132149A1 (en) | 2013-09-12 |
FI20125254A (en) | 2013-09-10 |
CN104160119B (en) | 2016-08-31 |
CN104160119A (en) | 2014-11-19 |
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