EP1537300A1 - Hydraulischer ventilsteller zum betätigen eines gaswechselventils - Google Patents
Hydraulischer ventilsteller zum betätigen eines gaswechselventilsInfo
- Publication number
- EP1537300A1 EP1537300A1 EP03714677A EP03714677A EP1537300A1 EP 1537300 A1 EP1537300 A1 EP 1537300A1 EP 03714677 A EP03714677 A EP 03714677A EP 03714677 A EP03714677 A EP 03714677A EP 1537300 A1 EP1537300 A1 EP 1537300A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- piston
- valve
- valve actuator
- actuator according
- 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.)
- Granted
Links
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
- Hydraulic valve actuator for actuating a gas exchange valve
- the invention relates to a hydraulic valve actuator for actuating a gas exchange valve in a combustion cylinder of an internal combustion engine according to the preamble of claim 1.
- a hydraulic valve actuator of this type (DE 198 26 047 AI), also called an actuator or actuator
- the lower pressure chamber via which a displacement of the actuating piston in the direction of valve closing is effected, is constantly pressurized with pressurized fluid and which is closed -
- return provided upper pressure chamber via which a piston displacement in the direction of valve opening is effected, by means of control valves, preferably 2/2-way solenoid valves, specifically pressurized via the inlet with pressurized fluid or relieved to approximately ambient pressure via the return.
- the pressurized fluid is controlled by a Pressure supply device supplied.
- a first control valve connects the upper pressure chamber to a relief line opening into a fluid reservoir and a second control valve connects the upper pressure chamber to the pressure supply device.
- the upper pressure chamber is closed by the closed second control valve
- Gas exchange valve opens because the effective area of the actuating piston delimiting the upper pressure chamber is larger than the effective area of the actuating piston delimiting the lower pressure chamber, the size of the opening stroke depending on the formation of the electrical control signal applied to the second control valve and the opening speed of the fluid pressure entered by the pressure supply device depends.
- the control valves are switched over again to close the gas exchange valve.
- the upper pressure chamber which is shut off in relation to the pressure supply device, lies on the relief line, and the fluid pressure prevailing in the lower pressure chamber leads the actuating piston back to its upper end position, so that the gas exchange valve is closed by the actuating piston.
- valve brake which is connected to the valve member of the gas exchange valve or to the valve actuator.
- the valve brake which takes effect during a residual closing stroke of the valve member, has a hydraulic damping member with a fluid displacement volume flowing out via a throttle opening.
- the return of the upper pressure chamber is divided into two connected drain openings, axially spaced apart in the housing, of which a throttle point is assigned to the upper drain opening and the lower drain opening lies in the displacement path of the actuating piston such that it of this can be closed before reaching the upper end position.
- the throttle opening is realized with a pressure-controlled throttle, the control pressure of which is controlled by means of an electrically controlled, hydraulic pressure valve and an electronic control device which controls it, depending on the viscosity of the
- Displacement volume is set. This has the advantage that the valve member is braked before it reaches its closed position during the closing stroke, the braking effect being independent of the temperature and the associated viscosity of the fluid volume displaced via the throttle opening. Because the opening cross-section of the throttle opening increases with increasing temperature and thus with decreasing Viscosity is reduced, the flow rate of the displaced fluid volume through the throttle opening decreases to the same extent, so that the size of the abbreviation of the actuating piston remains approximately constant through the damping member.
- valve actuator for actuating a gas exchange valve in a combustion cylinder
- Internal combustion engine has the advantage that when the actuating piston closes, that is to say when the actuating piston moves into its upper end position, the lower outlet opening is closed by the actuating piston after covering a certain displacement path and thus the fluid from the upper pressure chamber only via the
- Throttle point can be pushed out. This reduces the displacement speed of the actuating piston, so that the gas exchange valve connected to the actuating piston reduces its closing speed and finally places the valve member on the valve seat with a significantly reduced ejection speed. Since the lower drain opening is arranged at a distance from the upper end position of the actuating piston, the braking process always begins when the valve member of the gas exchange valve is at a certain distance from the valve seat.
- the cross-section of the throttle opening can influence the size of the speed reduction.
- there is a slight change in the stroke of the valve due to manufacturing tolerances in the gas exchange valve or due to different thermal expansions of the valve parts
- Valve member of the gas exchange valve until it is placed on the valve seat of the gas exchange valve, so the sliding design of the lower drain opening enables automatic tolerance compensation.
- the start of braking which is triggered by the actuating piston when the lower drain opening closes, starts with a closing stroke of the actuating piston which is adapted to the changed valve member stroke so that the braking of the valve member is always the same in all closing operations of the gas exchange valve Position, based on the distance from the valve seat, is used, i.e. the valve member is braked over a constant braking distance that is independent of the Torlerance until it is placed on the valve seat.
- the displaceable design of the lower drain opening is realized in that the lower drain opening from one of the
- Radial bore penetrating the housing and a radial bore communicating with it is assembled in a compensating piston surrounding the actuating piston and displaceable relative to the latter.
- the compensating piston which is designed so that it is carried along by the actuating piston moving into the upper end position, delimits the upper pressure chamber axially together with the actuating piston on the one hand, and axially delimits a lockable compensating chamber axially with its annular end facing away from the upper pressure chamber.
- the compensation chamber is shut off via the displacement path of the actuating piston and, in turn, is released for fluid exchange when the compensating piston begins to be taken along by the actuating piston moving into its upper end position.
- the compensating piston can still move within limits when the lower drain opening is closed and adjusts the position of the lower drain opening that determines the use of the braking process with respect to the closed position of the gas exchange valve, so that braking is always at exactly the same distance from the valve element, regardless of tolerances or thermal expansion occurring in the gas exchange valve before the valve seat.
- the compensating chamber is connected to a fluid reservoir at least when the compensating piston is entrained by the adjusting piston moving into its upper end position.
- the connection between the compensation chamber and the fluid reservoir can also be permanent, but the restriction to the establishment of the connection only has the advantage of preventing the compensation piston from occurring when the entrainment of the compensation piston is inserted
- Friction between the compensating piston and the actuating piston is taken in at an early stage.
- the provision of the fluid reservoir has the additional advantage that the moving of the actuating piston out of its upper end position, which is associated with the opening of the gas exchange valve, takes place with a quite large displacement force, which after a displacement path determined by the fluid reservoir, namely when no more fluid volume can be pushed out of the compensation chamber into the reservoir, is reduced. Energy is saved by reducing the displacement force in the further displacement of the actuating piston; because after the initial opening of the gas exchange valve to open the gas exchange valve further, the actuating force is very much smaller than the actuating force that must be applied against the high internal pressure in the combustion cylinder when the gas exchange valve is initially opened.
- Fig. 1 shows a longitudinal section of one with a
- FIG. 2 shows the same representation as in FIG. 1 when the gas exchange valve begins to brake
- FIG. 3 shows the same representation as in FIG. 1 with the gas exchange valve fully closed
- FIG. 4 shows the same representation as in FIG. 1 of the modified valve actuator
- Fig. 5 shows a longitudinal section of one with a
- Fig. 6 is the same illustration as in Fig. 5 with the gas exchange valve completely closed.
- the hydraulic valve actuator shown schematically in FIG. 1 serves to actuate a gas exchange valve 10 in a combustion cylinder of an internal combustion engine.
- the gas exchange valve 10 has a valve stem 11 and a valve member 12 which is seated at the end of the valve stem 11 remote from the valve actuator and which cooperates with a valve seat 13 formed in the cylinder head of the combustion cylinder.
- the valve seat 13 encloses a valve opening 14 which is closed in a gas-tight manner when the valve member 12 is seated on the valve seat 13.
- the gas exchange valve 10 can be an inlet or an outlet valve of the combustion cylinder.
- the valve actuator also called an actuator, for actuating the gas exchange valve 10, which represents a double-acting working cylinder, has a hollow cylindrical housing 15 and an actuating piston 16, which is guided axially displaceably in the housing 15 and is fixedly connected to the valve stem 11 and in one 3 shows the shift end position, hereinafter referred to as the upper end position, which keeps the gas exchange valve 10 closed and in a shift end position shown in FIG. 1, hereinafter referred to as the bottom end position, the gas exchange valve 10 opens to the maximum.
- the actuating piston 16 axially delimits two volume-variable pressure chambers 17, 18 in the housing 15 with different effective areas, the effective area which limits the right pressure chamber in FIG. 1, hereinafter referred to as the upper pressure chamber 17, being larger than that
- the lower pressure chamber 18 is permanently connected to a pressure supply device 20 which supplies high pressure fluid, e.g. Hydraulic oil, supplies.
- the pressure supply device 20 is represented in simplified form by a high-pressure pump 19 which draws fluid from a fluid reservoir 21 and makes the high-pressure fluid available at the outlet 201 of the pressure supply device 20.
- the pressure supply device 20 usually also contains a memory and a check valve.
- the upper pressure chamber 17 has an inlet 22 and a return 23, the return 23 being connected to a first control valve 25 by means of a return line 24 and the inlet 22 being connected to a second control valve 27 via an inlet line 26.
- the first control valve 25 is connected on the outlet side to a return or relief line 28 leading to the fluid reservoir 21, while the second control valve 27 is connected on the inlet side to the outlet 201 of the pressure supply device 20.
- Both control valves 25, 27 are preferably designed as a 2/2-way solenoid valve with spring return.
- the return 23 is divided into two drain openings 231, 232 connected to one another and axially spaced apart in the housing 15.
- the upper drain opening 231 is one
- Throttle point 29 assigned, and the lower outlet opening 232 is arranged in the displacement of the actuating piston 16 that it can be closed by this at a defined distance before reaching the upper end position.
- the upper outlet opening 231 is also used as the inlet 22, so that the inlet line 26 is connected to the upper outlet opening 231.
- the return line 24 is connected to the lower outlet opening 232, and the inlet and return lines 26, 24 are connected to one another via a connecting line 30 in which the throttle point 29 is arranged.
- the inlet 22 is realized by a separate inlet opening 31 in the housing 15.
- the return line 24 connected to the first control valve 25 has two line branches 241, 242, of which one line branch 241 leads to the upper outlet opening 231 and the other line branch 242 leads to the lower outlet opening 232.
- the throttle point 29, symbolically drawn in the line branch 241, is advantageously realized by designing the upper outlet opening 231 as a throttle bore.
- the actuating piston 16 is enclosed by a compensating piston 32 which is displaceable relative to the actuating piston 16.
- Actuating piston 16 and compensating piston 32 are guided in an axially displaceable manner in a guide sleeve 33 which is fixed immovably in the housing 15.
- Compensating piston 32 together with the active surface of the adjusting piston 16, axially delimits the upper pressure chamber 17 and, with its annular end surface facing away from the upper pressure chamber 17, a compensating chamber 34 in the guide sleeve 33.
- the compensating piston 32 carries near its the upper one
- End facing pressure chamber 17 a stop 321, and the actuating piston 16 carries at its end forming the active surface a counter-stop 161, which interacts with the stop 321 for taking the equalizing piston 32 through the adjusting piston 16 moving into the upper end position.
- the lower drain opening 232 is composed of a first radial bore 35 in the housing 15, a second radial bore 36 in the guide sleeve 33 and a third radial bore 37 in the compensating piston 32.
- the compensating chamber 34 is shut off via the displacement path of the actuating piston 16 and is only released for fluid drainage or inflow by the actuating piston 16 moving into its upper end position when the compensating piston 32 begins to be carried along.
- a compensation channel 39 is incorporated in the guide sleeve 33, which connects the second radial bore 36 to a radial bore 40 in the guide sleeve 33 which is spaced apart and opens towards the actuating piston 16.
- the actuating piston 16 carries an annular groove 41 which has such an axial groove width that it establishes a connection between the mouth of the radial bore 40 and the compensating chamber 34 in a certain relative position of the actuating piston 16 and compensating piston 32.
- the annular groove 41 is placed on the actuating piston 16 in such a way that the connection is established when the compensating piston 32 begins to be taken along by the actuating piston 16, that is to say with the counter stop 161 abutting against the abutment 321, and is only released again when the actuating piston 16 is in position has moved something out of its upper end position.
- a spacer sleeve 42 is inserted into the housing 15 within the upper pressure chamber 17 and forms a stop for the compensating piston 32.
- the compensating piston 32 can thus move between the bottom of the compensating chamber 34 formed by the guide sleeve 33 and the spacer sleeve 42. Since the spacer sleeve 42 is located in the region of the upper outlet opening 231 and the inlet opening 31, a radial bore 43 is provided in the spacer sleeve 42, as shown in FIG. 1, which corresponds to the upper inlet opening 231 or to the outlet opening 31 which is identical to this , 4, two radial bores 43 are provided, one of which is aligned with the upper outlet opening 231 and one with the inlet opening 31.
- the hydraulic valve actuator works as follows:
- valve actuator is shown in its lower end position adjusting piston 16, in which
- Gas exchange valve 10 is opened to the maximum.
- the control valves 25, 27 are switched to their position shown in FIG. 1.
- the first control valve 25 is open and thus the upper pressure chamber 17 is connected to the fluid reservoir 21 via the return 23 (upper and lower outlet opening 231, 232), the return line 24 and the relief line 28.
- the second control valve 27 is closed. Since the lower pressure chamber 18 is constantly under the fluid pressure generated by the pressure supply device 20, the actuating piston 16 is shifted to the right in FIG. 1 and the gas exchange valve 10 moves in the closing direction. This creates fluid from the upper pressure chamber 17 pushed out, which flows on the one hand via the lower outlet opening 232 and on the other hand via the upper outlet opening 231 and the throttle point 29 into the return line 24 and reaches the fluid reservoir 21 via the relief line 28.
- the actuating piston 16 passes over the radial bore 37 in the compensating piston 32 and thus closes the lower outlet opening 232.
- the fluid can now only flow into the return line 24 via the upper outlet opening 231 and via the throttle point 29.
- the throttle point 29 allows only a small amount of fluid to flow away per unit of time, so that the actuating piston 16 and the gas exchange valve 10 are braked.
- the adjusting piston 16 continues, now at a reduced speed, to perform a displacement movement into its upper end position until the gas exchange valve 10 is closed, ie the valve member 12 strikes the valve seat 13.
- the shift stroke at which the actuating piston 16 begins to brake depends on the position of the actuating piston 16 relative to the compensating piston 32.
- the compensation piston 32 can move between the bottom of the compensation chamber 34 and the spacer sleeve 42.
- the compensating piston 32 assumes any position between the chamber bottom and the spacer sleeve 42. If the equalizing piston 32 is too far to the left in the illustration in FIG. 1, when the valve closes, the adjusting piston 16 with its counter stop 161 hits the stop 321 of the equalizing piston 32.
- the annular groove 41 in the adjusting piston 16 provides a connection between the also with fluid-filled compensation chamber 34 and the radial bore 40 in the guide sleeve 33, which in turn is connected to the lower drain opening 232 via the compensation channel 39.
- the compensation piston 32 is now able to move.
- the actuating piston 16 moves with the compensation piston 32 until the valve member 12 of the gas exchange valve 10 lies tight against the valve seat 13. Since the compensating piston 32 is carried along, the connection between the compensating chamber 34 and the lower drain opening 232 remains through the annular groove 41 (FIG. 3).
- the first control valve 25 is closed and the second control valve 27 is opened.
- the upper pressure chamber 17 is now under the fluid pressure supplied by the pressure supply device 20. Since the effective area of the actuating piston 16 delimiting the upper pressure chamber 17 is larger than the effective area of the actuating piston 16 delimiting the lower pressure chamber 18, the actuating piston 16 moves to the left in the drawing and the gas exchange valve 10 is opened.
- Compensation chamber 34 is connected via the annular groove 41 to the lower drain opening 232 and this via the throttle point 29 to the upper pressure chamber 17, so that the same pressure prevails in the compensation chamber 34 as in the upper pressure chamber 17. Since the two the compensation chamber 34 and the upper pressure chamber 17 delimiting active surfaces of the compensating piston 32 are equalized, the compensating piston 32 is pressure-compensated, so that no resulting displacement force on the compensating piston 32 arises. The pressure build-up in the compensation chamber 34 takes place somewhat later due to the throttle point 29, so that the compensation piston 32 carries out a slight movement to the left. As soon as the control piston 16 has moved so far that the annular groove 41 cancels the connection to the compensation chamber 34, the compensation chamber 34 is shut off, so that the compensation piston 32 remains in the position reached.
- the compensating piston 32 is thus adjusted, and the radial bore 37 in the compensating piston 32 belonging to the lower outlet opening 232 has a fixed position with respect to the closed state of the gas exchange valve 10, so that the actuating piston 16 always closes the radial bore 37 at a fixed distance before reaching its end position and thus on the gas exchange valve 10, the braking process always starts at a fixed distance of the valve member 12 from the valve seat 13. If the compensating piston 32 was too far to the right during the closing process in the illustration of FIGS. 1-3, it is thereby that the compensating piston 32 performs a slight movement to the left when the gas exchange valve 10 is opened, as described, the compensating piston 32 during the following closing and The opening process of the gas exchange valve 10 is adjusted as described.
- Gas exchange valve 10 is identical in construction and mode of operation to the valve actuator described above, so that the same components are provided with the same reference numerals. Through a constructive measure, this valve actuator has the additional advantage that it
- Gas exchange valve 10 opens with a high actuating force, so that the valve member 12 lifts quickly and safely against the high internal pressure in the combustion cylinder of the internal combustion engine from the valve seat 13, and that after the valve member 12 has been lifted off the valve seat 13 and the internal pressure in the combustion cylinder that collapses, the valve member 12 moved with low actuating force.
- the compensating piston 32 in the guide sleeve . 33 limited equalization chamber 34 not - as shown in FIGS.
- 1-3 connectable to the return 23 via the annular groove 41 in the actuating piston 16, but with a fluid reservoir 44 which both receives a fluid volume from the equalization chamber 34 and fills it into the equalization chamber 34 ,
- a fluid reservoir 44 which both receives a fluid volume from the equalization chamber 34 and fills it into the equalization chamber 34
- two aligned radial bores 45, 46 are present in the housing 15 and in the guide sleeve 33, which are connected to a connecting line 47 leading to the fluid reservoir 44.
- the fluid reservoir 44 is designed as a separate component, but can also be integrated in the housing 15 of the valve actuator.
- connection between compensating chamber 34 and fluid reservoir 44 again takes place via the annular groove 41 when the compensating piston 32 is taken along by the actuating piston 16 moving into its upper end position, that is to say when the counter stop 161 on the actuating piston 16 hits the stop 321 on the compensating piston 32.
- the fluid reservoir 44 has a control chamber 48 with two axially opposite chamber openings 481, 482 as well as a control member 49 axially displaceable in the control chamber 48 for alternately closing the two chamber openings 481, 482.
- the connecting line 47 to the radial bore 45 in the housing 15 is connected to one chamber opening 481, while the other chamber opening 482 is connected to the relief line 28 via a connecting line.
- the connection to the relief line 28 is made in a line section between the outlet of the first control valve 25 and a pressure regulating valve 51 arranged in the relief line 28.
- the pressure control valve 51 ensures that at the chamber opening 481 there is always a low fluid pressure of approx. 0.1 MPa.
- control member 49 is designed as a ball, which alternately sits on a frustoconical valve seat upstream of the chamber openings 481 and 482 and is thus able to close the chamber openings 481, 482.
- control chamber 48 there is also a radial bore 52 which is connected to the connecting line 47 via a throttle 53.
- the radial bore 52 is in the
- Control chamber 48 placed so that it is close to the chamber opening 481, but is not covered by the control member 49 when the chamber opening 481 is closed by the control member 49.
- the two control valves 25, 27 are switched over so that the first control valve 25 closes and the second control valve 27 opens.
- a fluid pressure builds up in the upper pressure chamber 17, which acts on the active surface of the actuating piston 16 and on the end face of the compensating piston 32.
- the displacement force in the opening direction of the gas exchange valve 10 is high.
- the displacement movement of the compensating piston 32 reduces the compensating chamber 34.
- the fluid is pushed out into the control chamber 48, whereby the spherical control member 49 moves to the right in the control chamber 48.
- the fluid in the control chamber 48 is pushed out into the relief line 28 via the chamber opening 482.
- fluid can also reach the relief line 28 directly from the compensation chamber 32 via the radial bore 52, but the throttle 53 ensures that this is only a very small amount of fluid. With the help of a check valve assigned to the throttle 53, this low fluid flow can be completely prevented. As soon as the control member 49 closes the other chamber opening 482, no more fluid can be pushed out of the compensating chamber 34, and the compensating piston 32 can no longer carry out a displacement movement. The displacement path of the compensating piston 32 can thus be adjusted via the volume in the control chamber 48.
- the moving adjusting piston 16 lifts off the equalizing piston 32.
- the displacement force acting on the actuating piston 16 is significantly reduced, since only the effective area of the actuating piston 16 delimiting the upper pressure chamber 17 is decisive for generating the displacement force.
- Guide sleeve 33 can be acted upon with fluid pressure from the feed line 26, only serves to increase the wall thickness of the compensating piston 32 over a large area of the compensating piston 32 in order to achieve better producibility.
- the outer diameter of the compensating piston 32 can also be produced without this shoulder 322 if the desired force ratio allows a sufficiently large wall thickness of the compensating piston 32 when the gas exchange valve 10 is initially opened and the gas exchange valve 10 is subsequently opened further.
- valve actuator shown in FIGS. 5 and 6 can be modified such that the annular groove 41 in the actuating piston 16 is omitted and the
- Compensation chamber 34 is permanently connected to the control chamber 48. This does not change the mode of operation of the valve actuator. However, there is the possibility that the compensating piston 32 is taken too early due to friction between the compensating piston 32 and the actuating piston 16. However, this can be avoided by adhering to manufacturing tolerances.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Control Of Fluid Pressure (AREA)
- Fluid-Driven Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10239747 | 2002-08-29 | ||
DE10239747A DE10239747A1 (de) | 2002-08-29 | 2002-08-29 | Hydraulischer Ventilsteller zum Betätigen eines GAswechselventils |
PCT/DE2003/000699 WO2004022929A1 (de) | 2002-08-29 | 2003-03-05 | Hydraulischer ventilsteller zum betätigen eines gaswechselventils |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1537300A1 true EP1537300A1 (de) | 2005-06-08 |
EP1537300B1 EP1537300B1 (de) | 2006-06-07 |
Family
ID=31502109
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03714677A Expired - Lifetime EP1537300B1 (de) | 2002-08-29 | 2003-03-05 | Hydraulischer ventilsteller zum betätigen eines gaswechselventils |
Country Status (5)
Country | Link |
---|---|
US (1) | US7007642B2 (de) |
EP (1) | EP1537300B1 (de) |
JP (1) | JP4443410B2 (de) |
DE (2) | DE10239747A1 (de) |
WO (1) | WO2004022929A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005056012A1 (de) * | 2005-11-24 | 2007-06-06 | Volkswagen Ag | Hydraulische Ventilsteuervorrichtung für ein Hubventil |
DE102006012067B4 (de) * | 2006-03-16 | 2016-03-24 | Volkswagen Ag | Hydraulische Ventilbetätigungsvorrichtung für ein Gaswechselventil |
CN101743423A (zh) * | 2007-05-18 | 2010-06-16 | 恩菲尔德技术责任有限公司 | 电子控制阀和包含该电子控制阀的系统 |
DE102008054014A1 (de) * | 2008-10-30 | 2010-05-06 | Man Nutzfahrzeuge Aktiengesellschaft | Gaswechselventil für Brennkraftmaschinen |
US8925502B1 (en) * | 2010-01-22 | 2015-01-06 | Brp Us Inc. | Hydraulically actuated valve assembly for an engine |
US9725994B2 (en) * | 2013-10-28 | 2017-08-08 | Halliburton Energy Services, Inc. | Flow control assembly actuated by pilot pressure |
CN103850743B (zh) * | 2014-04-02 | 2016-01-06 | 广西玉柴机器股份有限公司 | 可变气门正时驱动装置 |
CN106703928B (zh) * | 2016-12-28 | 2022-07-15 | 沪东重机有限公司 | 由伺服油直接驱动的排气阀控制执行系统 |
US10227951B2 (en) | 2017-02-02 | 2019-03-12 | Woodward, Inc. | Limited flow thrust reverser actuating |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3836725C1 (de) * | 1988-10-28 | 1989-12-21 | Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
EP0441100B1 (de) | 1990-02-08 | 1993-04-28 | GebràDer Sulzer Aktiengesellschaft | Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine |
US5275136A (en) * | 1991-06-24 | 1994-01-04 | Ford Motor Company | Variable engine valve control system with hydraulic damper |
US5231959A (en) * | 1992-12-16 | 1993-08-03 | Moog Controls, Inc. | Intake or exhaust valve actuator |
US5410994A (en) * | 1994-06-27 | 1995-05-02 | Ford Motor Company | Fast start hydraulic system for electrohydraulic valvetrain |
DK0767295T3 (da) | 1995-10-03 | 2000-06-05 | Wortsilo Nsd Schweiz Ag | Hydraulisk ventildrev |
DE19826047A1 (de) | 1998-06-12 | 1999-12-16 | Bosch Gmbh Robert | Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen |
US6044815A (en) * | 1998-09-09 | 2000-04-04 | Navistar International Transportation Corp. | Hydraulically-assisted engine valve actuator |
DE10201167A1 (de) | 2001-10-24 | 2003-05-15 | Bosch Gmbh Robert | Vorrichtung zur Steuerung eines Öffnungsquerschnitts in einem Verbrennungszylinder einer Brennkraftmaschine |
-
2002
- 2002-08-29 DE DE10239747A patent/DE10239747A1/de not_active Withdrawn
-
2003
- 2003-03-05 JP JP2004533189A patent/JP4443410B2/ja not_active Expired - Fee Related
- 2003-03-05 EP EP03714677A patent/EP1537300B1/de not_active Expired - Lifetime
- 2003-03-05 US US10/493,858 patent/US7007642B2/en not_active Expired - Fee Related
- 2003-03-05 DE DE50303725T patent/DE50303725D1/de not_active Expired - Lifetime
- 2003-03-05 WO PCT/DE2003/000699 patent/WO2004022929A1/de active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO2004022929A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE10239747A1 (de) | 2004-03-11 |
US7007642B2 (en) | 2006-03-07 |
WO2004022929A1 (de) | 2004-03-18 |
JP2005537428A (ja) | 2005-12-08 |
EP1537300B1 (de) | 2006-06-07 |
JP4443410B2 (ja) | 2010-03-31 |
DE50303725D1 (de) | 2006-07-20 |
US20050028763A1 (en) | 2005-02-10 |
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