CN102713173A - Electrohydraulic actuator - Google Patents
Electrohydraulic actuator Download PDFInfo
- Publication number
- CN102713173A CN102713173A CN2010800610394A CN201080061039A CN102713173A CN 102713173 A CN102713173 A CN 102713173A CN 2010800610394 A CN2010800610394 A CN 2010800610394A CN 201080061039 A CN201080061039 A CN 201080061039A CN 102713173 A CN102713173 A CN 102713173A
- Authority
- CN
- China
- Prior art keywords
- high pressure
- pressure control
- piston
- low
- control valves
- 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
- 230000002000 scavenging effect Effects 0.000 claims description 29
- 239000012530 fluid Substances 0.000 claims description 27
- 239000003792 electrolyte Substances 0.000 claims description 26
- 210000000635 valve cell Anatomy 0.000 claims description 6
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 230000005611 electricity Effects 0.000 claims 1
- 230000001276 controlling effect Effects 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010304 firing Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
- F01L25/08—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by electric or magnetic means
Abstract
An electrohydraulic actuator is provided, which comprises a working cylinder (22), having a piston (23) comprising a first and second piston surface (231, 232) displaceable in said working cylinder and two working chambers (24, 25) designed in the working cylinder (22) and bounded by the piston (23), as well as electric control valves. Of the two working chambers (24, 25), a first working chamber (24) that is permanently subject to high pressure is bounded by the first piston surface (231) and a second working chamber (25) is bounded by the larger second piston surface (232). The control valves alternately establish a connection of the second working chamber (25) to high pressure and low pressure. In order to achieve comprehensive options for controlling the piston (23) over the stroke path thereof, at least one of the connections of the second working chamber (25) to high and low pressure is established with a plurality of control valves, wherein both a plurality of high pressure control valves (30, 31) can establish the connection to high pressure and a plurality of low pressure control valves (32, 33) can establish the connection to low pressure.
Description
Technical field
The present invention relates to a kind of according to claim 1 electrolyte type actuator as described in the preamble.
Background technique
The electrolyte type actuator of the known scavenging air valve that is used for controlling combustion engine has a clutch release slave cylinder, one can be that constitute in clutch release slave cylinder in the axially movable piston with first piston face and second piston area bigger than first piston face of clutch release slave cylinder, two, by the working room of piston area gauge, and electrically operated valve.At this, the first piston of piston in the face of first working room's gauge that for good and all is loaded the fluid that is under the high pressure and second piston area to second working room's gauge that is connected with control valve.Fluid under the control valve that is configured to solenoid valve is selectively set up second working room and is in high pressure and be in low pressure under being connected of fluid.If second working room is loaded the fluid that is under the high pressure, piston moves out and causes opening of scavenging air valve from its upper dead center position so.If second working room is ended with respect to high pressure and low pressure, so piston remain in its current stroke position and thus this scavenging air valve remain in its current open position.Cause that piston gets back to the backhaul in its upper dead center position if second working room, is in high pressure in first working room so by off-load, scavenging air valve is closed again thus.
Summary of the invention
Especially, it has brought tangible advantage when being used for the scavenging air valve of controlling combustion engine according to the electrolyte type actuator with characteristic of claim 1 of the present invention.Through a plurality of preferably have identical or different flow cross section and can be personalized ground time synchronization and/or the time controlled control valve in ground that staggers for example, allow the stroke of control piston very delicately and on purpose the lift curve of scavenging air valve exerted one's influence thus.Through a plurality of high pressure control valves with identical or different flow cross section; Permission is through control these high pressure control valves than the little stroke through unique much better ground of a high pressure control valve regulating piston personalizedly, and this unique high pressure control valve must have a very large flow cross section that is used for opening fast stroke.Because the stroke of scavenging air valve is corresponding to the opening between stroke by the Fluid Volume of dosage of piston, so can be in the mode of execution of high pressure control valve than regulate the less Fluid Volume of scavenging air valve and small stroke thus better through a unique high pressure control valve with corresponding big flow cross section with different flows or through flow cross section.Through high pressure control valve postpone in time close, the end of the opening procedure of scavenging air valve is not conversion time through the dynamic control valve of height but carry out through approaching of continuing suddenly.Reduced the overshoot tendency of scavenging air valve thus.Allow the maximum stroke very accurately regulate scavenging air valve thus.Different with the known technology of the overshoot that is used to avoid scavenging air valve, realized the obviously more accurate dosage of the convection current scale of construction, produce the more accurate stroke precision of electrolyte type actuator thus.
Through a plurality of low-pressure control valves with identical or different flow cross section, the lift curve that allows the backhaul of much sensitive ground control piston and influence scavenging air valve accurately is the trend in the zone endways.The scavenging air valve break of hydraulic pressure, it avoids the hard collision of valve cell to valve seat, also allows to realize very simply by a plurality of low-pressure control valves.
Can be implemented in the favourable expansion scheme and the improvement project of the actuator that provides in the claim 1 through the measure of listing in other claims.
According to a kind of favourable mode of execution of the present invention, at least one high pressure control valve in said a plurality of high pressure control valves is connected on the pressure duct of direct high pressure at input side and at least one high pressure control valve is connected on the discharge aperture that is passed in said first working room at input side.Said discharge aperture is arranged in the said clutch release slave cylinder in this wise, makes said piston load the mobile stroke that triggers, confirm from one of piston by the high pressure to said second working room and begins to seal said discharge aperture.The corresponding high pressure control valve that is connected on the corresponding discharge aperture that is crossed takes off coupling with the fluid input of leading to second working room thus, makes input through the Fluid Volume that is classified to reduce can be classified to delay and the mobile distance of regulating piston accurately.Effective stroke gauge can be realized thus and the classification stroke of definite step can be realized having through appropriate control.
According to a kind of favourable mode of execution of the present invention, at least one low-pressure control valve in said a plurality of low-pressure control valves is connected with said second working room and at least one low-pressure control valve is connected on the discharge aperture that is passed in said second working room at input side at input side.Said discharge aperture is arranged in the said clutch release slave cylinder in this wise, makes said piston seal said discharge aperture since one by the backhaul that trigger, that confirm of the high pressure unloading to said second working room.If piston does not also arrive this stroke position, fluid can carry out through the flow cross section sum of these low-pressure control valves of opening from the discharge of second working room so.Along with each quilt in these discharge apertures crosses, the discharge through being connected to the low-pressure control valve on the discharge aperture by by and discharge and only carry out through flow cross section remainder, that be reduced.Discharge thus cumulatively by throttling, in second working room, form back pressure thus, this back pressure is carried out throttling to the stroke speed of piston.Thus through low-pressure control valve allow influence scavenging air valve lift curve stub area and realize the valve braking with simple mode, this valve is braked when valve cuts out fast and is avoided valve cell to strike on the valve seat firmly.
Description of drawings
The present invention is according at length being set forth in the embodiment illustrated in the accompanying drawings specification below.It illustrates with schematic representation respectively:
Fig. 1 to 4 illustrates the longitudinal section of the electrolyte type actuator that is used for being connected with the Gas Exchange Process of Internal Combustion Engine valve respectively with four embodiments altogether.
Embodiment
The cylinder cap 11 of deflagrating jar partly is shown with the longitudinal section in Fig. 1 to 4, and this deflagrating jar surrounds a firing chamber 12 with a reciprocating piston that in deflagrating jar, is directed to.In cylinder cap 11, be configured with a gas channel 13 that feeds in the firing chamber 12, the feeding opening of this gas channel is by 14 controls of a scavenging air valve.Scavenging air valve 14 can be inlet or outlet valve.Scavenging air valve 14 comprises the seat ring 15 and the valve cell 18 that has valve rod 19 and be arranged in the valve disc 20 on valve rod 19 ends that are arranged in the cylinder cap 11; Valve opening 16 is configured in this seat ring with the valve seat 17 that surrounds valve opening 16, and this valve disc and valve seat 17 actings in conjunction are to discharge and draught excluder opening 16.
The valve cell 18 of scavenging air valve 14 is by 21 operations of electrolyte type actuator.Actuator 21 have a clutch release slave cylinder 22, piston that can in clutch release slave cylinder 22, axially be directed to movably 23, two that in clutch release slave cylinder 22, constitute, by the working room 24,25 and the electrically operated valve of piston 23 gauges.Piston 23 is with 231 pairs first working room's 24 gauges of first piston face and with second piston area 232 pair second working room 25 gauges bigger than this piston area 231.First working room 24 for good and all is loaded the fluid that is under the high pressure, and these control valves are connected in second working room 25 and set up alternatively be in high pressure under fluid be in low pressure under being connected of fluid.
For fluid high-pressure and low pressure are provided, be provided with a fluid storage 26, high-pressure service pump 27, a pressure duct 28 and an offloading pipeline 29.This high-pressure service pump 27 is from fluid storage 26 draw fluid and will be in fluid storage under the high pressure pressure duct 28.Low pressure or offloading pipeline 29 will be transmitted back to the fluid storage 26 from the fluid that second working room 25 discharges.For example, the low pressure in the offloading pipeline 29 is between 1 to 6 crust.High pressure in second working room 25 and pressure duct 28 with offloading pipeline 29 in being connected in (setting up through control valve among all embodiments of their electrolyte type actuators 21 in Fig. 1 to 4) of low pressure, at least one during these connect set up through a plurality of control valves.In the embodiment in figure 1, being connected through a plurality of high pressure control valves of second working room 25 and high pressure set up, Fig. 1 exemplified two high pressure control valves 30,31 in these high pressure control valves are shown.Second working room 25 carried out with being connected through a unique low-pressure control valve 32 of low pressure.A plurality of, be connected on the pressure duct 28 of direct high pressure at input side at these two high pressure control valves 30,31 parallelly connectedly.A plurality of high pressure control valves 30,31 not only can have identical flow cross section but also can have the different flows cross section and personalized ground, for example controlled with synchronously or in time staggering in time.The electric control of all control valves (it for example is configured to two-position two-way solenoid valve at this) is through carrying out at this unshowned motor control assembly.
If low-pressure control valve 32 by control and be closed thus and high pressure control valve 30,31 by control and be opened thus, the big fluid volume that is in so under the high pressure flow in second working room 25.Piston 23 moves and scavenging air valve 14 is opened apace the dead center position with high speed from it, thereby the lift curve of this scavenging air valve has precipitous input side edge.If one of two high pressure control valves 30,31 are closed during stroke of piston, the Fluid Volume that flows into so again in second working room 25 obviously reduces.Velocity of piston descends, and the mobile distance of piston 23 can be accurate many ground are controlled.Simultaneously, piston 23 to the stroke end position of hoping (this stroke end position corresponding to scavenging air valve confirm open) in sail into and can be reduced through the high pressure control valve 30 that keeps or 31 unexpected closing significantly by the overshoot of very accurately control and piston 23.The overshoot tendency of the valve cell 18 of scavenging air valve 14 in the open position of confirming is reduced thus.
The embodiment of the electrolyte type actuator 21 among Fig. 2 is modified with respect to the electrolyte type actuator in Fig. 1; Be that high pressure control valve 31 is free of attachment on the fluid circuit 28 at input side, but be connected on the discharge aperture 34 that in the length of stroke of piston 23, is passed in first working room 24.Thus a plurality of high pressure control valves (Fig. 2 exemplified two control valves 30,31 wherein are shown) in, at least one high pressure control valve is connected on the pressure duct 28 of direct high pressure at input side and at least one high pressure control valve is connected on the discharge aperture 34 at input side.At this, a plurality of discharge apertures 34 can be passed in second working room 25 and be connected with the input end of other high pressure control valve respectively, and the output terminal of the high pressure control valve that these are other is connected to again in second working room 25.Discharge aperture 34 is arranged in the clutch release slave cylinder 22, and promptly this discharge aperture is sealed by piston 23 since a mobile stroke that comes out from upper dead center position definite, that triggered by the high pressure loading to second working room 25.This position of piston 23 (wherein discharge aperture 34 is closed) marks in Fig. 2 dotted line and representes through 35.If high pressure control valve 31 is opened and high pressure control valve 30 is closed when low-pressure control valve 32 is closed, piston 23 can move in the stroke position 35 the biglyyest so.Can realize the classification stroke with definite step of piston 23 thus through a plurality of discharge apertures (at wherein discharge aperture 34 shown in Fig. 4).Additionally, can influence the stroke characteristic of piston 23 through control to the suitable personalization of high pressure control valve 30,31.
In electrolyte type actuator 21 according to Fig. 3; Cancelled the addition thereto that is used for when the upper dead center position from piston moves out, influencing piston 23, thereby second working room 25 is connected on the pressure duct 28 with a required big flow cross section of fast moving motion for piston 23 through a unique high pressure control valve 30.On the contrary, second working room 25 with set up being connected of offloading pipeline 29 of guiding low pressure through a plurality of low-pressure control valves, Fig. 3 exemplified two low pressure valves 32,33 wherein are shown.In a plurality of low- pressure control valves 32,33; At least one low-pressure control valve (is low-pressure control valve 32 at this) is connected with second working room 25 at input side, and at least one low-pressure control valve (is low-pressure control valve 33 at this) is connected on the discharge aperture 34 that in the stroke range of piston 23, is passed in second working room 25 at input side.Discharge aperture 34 is arranged in the clutch release slave cylinder 22, makes piston 23 begin to seal discharge aperture from the backhaul that the high pressure unloading of confirming by second working room 25 triggers.The stroke position of piston 23 (beginning discharge aperture 37 from this stroke position is closed) is illustrated among Fig. 3 dotted line and representes with 38.Low- pressure control valve 32,33 can have identical flow cross section, but also can be provided with the different flows cross section.With staggering controlled again by personalization ground, for example time synchronization or time for low-pressure control valve 32,33.Also can be connected at discharge aperture of input side and each at this other low- pressure control valve 32,33, these discharge apertures arrange stackedly up and down that in clutch release slave cylinder piston 23 is enclosed in front and back discharge aperture 37 in succession in the length of stroke successively thus.
If high pressure control valve 30 is closed and two low- pressure control valves 32,33 are opened, fluid carries out through two low-pressure control valves 32 from the discharge of second working room 25 in the backhaul of piston 23 so.Big discharge cross section obtains and the past very apace swivel motion of piston 23 through the flow cross section sum of low- pressure control valve 32,33, and scavenging air valve 14 is closed thus apace.If piston 23 arrives stroke position 38, discharge aperture 37 ends through piston 23 so.Fluid only can be discharged through the flow cross section obviously littler than cross section sum of low-pressure control valve 32.This is discharged obviously more consumingly by throttling, thus build-up pressure and the speed of closing movement carried out throttling in second working room 25.Low-pressure control valve 32 can be used for the braking of control piston 23 and cause closing of scavenging air valve 14 thus, and wherein valve disc 20 is not to impact firmly on the valve seat 17.When the low-pressure control valve 32 of last active is constructed to Proportional valve, obtain the other control possibility in the backhaul stage of piston 23.
In the embodiment of the electrolyte type actuator 21 shown in Fig. 4, not only realize in combination according to the structural measure in the actuator 21 of Fig. 2 but also according to the structural measure in the actuator 21 of Fig. 3.Two working rooms 25 carried out with being connected through at least two high pressure control valves 30,31 of high pressure, and a high pressure control valve in these high pressure control valves is connected on the pressure duct 28 and another high pressure control valve is connected in the stroke path of piston 23 on the discharge aperture 34 that feeds in first working room 24 at input side at input side.At outlet side, two high pressure control valves 30,31 are connected with two working rooms 25.Second working room 25 carried out with being connected through at least two low- pressure control valves 32,33 of low pressure, and a low-pressure control valve in these low-pressure control valves is connected in second working room 25 and second low-pressure control valve 33 is connected on the discharge aperture 37 that in the length of stroke of reciprocating piston 23, is passed in first working room 24 at input side.Two low- pressure control valves 32,33 are connected with offloading pipeline 29 at outlet side.In this electrolyte type actuator 21, the possibility that above-mentioned being used to influences the lift curve of scavenging air valve provides with sum.Conversion ground, high pressure control valve 30,31 also can be connected shown in Fig. 1 like it.
In described electrolyte type actuator 21, opening stroke and still can otherwise being affected of piston 23 for example put the annular piston on piston 23 through a seat, like it describing among DE 10143952A1, Fig. 2.In addition, a pair of outlet valve or a pair of inlet valve that electrolyte type actuator 21 also can controlling combustion engine, to be the piston 23 that is configured to classification or stepped piston act on valve last coupling unit be connected with one its mode.So-called " double plate " for example described in DE 10147305A1.
Claims (11)
1. the electrolyte type actuator comprises: a clutch release slave cylinder (22); One can axially movable piston (23) in this clutch release slave cylinder (22), and this piston has first piston face (231) and second piston area (232) bigger than this first piston face; Two working rooms (24 that in this clutch release slave cylinder (22), constitute; 25), first working room (24) that for good and all is loaded the fluid that is under the high pressure of in these working rooms by this first piston face (231) gauge and one second working room (25) by this second piston area (232) gauge; With the control valve that is connected to the electricity in this second working room (25); These control valves set up alternatively be in high pressure under fluid be in low pressure under being connected of fluid; It is characterized in that at least one in being connected of said second working room (25) and high pressure and low pressure connects through a plurality of control valves to be set up.
2. according to the electrolyte type actuator of claim 1, it is characterized in that said second working room (25) set up with being connected through a plurality of high pressure control valves (30,31) of high pressure.
3. according to the electrolyte type actuator of claim 1 or 2, it is characterized in that said second working room (25) set up with being connected through a plurality of low-pressure control valves (32,33) of low pressure.
4. according to the electrolyte type actuator of claim 2 or 3, it is characterized in that said a plurality of high pressure control valves (30,31) are connected on the pressure duct (28) of direct high pressure at input side parallelly connectedly.
5. according to the electrolyte type actuator of one of claim 2 to 4; It is characterized in that; Said a plurality of high pressure control valve (30; 31) pressure duct (28) that at least one high pressure control valve (30) in is connected to direct high pressure at input side is gone up and at least one high pressure control valve (31) is connected to that a discharge aperture (34) that in the scope of the length of stroke of said piston (23), is passed in said first working room (24) is gone up and said discharge aperture (34) is arranged in the said clutch release slave cylinder (22) in this wise, makes said piston (23) load the mobile stroke that triggers, confirm since one by the high pressure to said second working room (25) and seals said discharge aperture.
6. according to the electrolyte type actuator of one of claim 3 to 5; It is characterized in that; Said a plurality of low-pressure control valve (32; 33) at least one low-pressure control valve (32) in is connected with said second working room (25) and at least one low-pressure control valve (33) is connected at input side that a discharge aperture (37) that in the scope of the length of stroke of said piston (23), is passed in said second working room (25) is gone up and said discharge aperture (37) is arranged in the said clutch release slave cylinder (22) in this wise at input side, makes said piston (23) seal said discharge aperture since one by the backhaul that trigger, that confirm of the high pressure unloading to said second working room (25).
7. according to the electrolyte type actuator of one of claim 2 to 6, it is characterized in that said a plurality of high pressure control valves (30,31) have the different flows cross section.
8. according to the electrolyte type actuator of one of claim 3 to 7, it is characterized in that said a plurality of low-pressure control valves (32,33) have the different flows cross section.
9. according to the electrolyte type actuator of one of claim 2 to 8, it is characterized in that said a plurality of high pressure control valves (30,31) can be controlled individually.
10. according to the electrolyte type actuator of one of claim 3 to 9, it is characterized in that said a plurality of low-pressure control valves (32,33) can be controlled individually.
11. electrolyte type actuator according to one of claim 2 to 10; It is characterized in that; Said piston (23) is connected with the valve cell (18) of at least one scavenging air valve (14) of internal-combustion engine in this wise; Make said low-pressure control valve (32,33) when closing through in said a plurality of high pressure control valves (30,31) at least one open said at least one scavenging air valve (14) and at said a plurality of high pressure control valves (30; When 31) closing when in the said low-pressure control valve (32,33) at least one opened said at least one scavenging air valve (14) be closed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009046943.5 | 2009-11-20 | ||
| DE102009046943A DE102009046943A1 (en) | 2009-11-20 | 2009-11-20 | Electrohydraulic actuator |
| PCT/EP2010/006325 WO2011060855A2 (en) | 2009-11-20 | 2010-10-15 | Electrohydraulic actuator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102713173A true CN102713173A (en) | 2012-10-03 |
| CN102713173B CN102713173B (en) | 2015-06-17 |
Family
ID=43828055
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080061039.4A Expired - Fee Related CN102713173B (en) | 2009-11-20 | 2010-10-15 | Electrohydraulic actuator |
Country Status (4)
| Country | Link |
|---|---|
| CN (1) | CN102713173B (en) |
| DE (1) | DE102009046943A1 (en) |
| FI (1) | FI126134B (en) |
| WO (1) | WO2011060855A2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015501905A (en) * | 2011-12-16 | 2015-01-19 | サステインエックス インク．Ｓｕｓｔａｉｎｘ Ｉｎｃ． | Valve actuation in compressed gas energy storage and recovery systems. |
| SE544645C2 (en) * | 2020-03-02 | 2022-10-04 | Freevalve Ab | Actuator and method for operating an actuator |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0455937A1 (en) * | 1990-05-11 | 1991-11-13 | Mitsubishi Jukogyo Kabushiki Kaisha | Valve driving apparatus of an internal combustion engine |
| US6148778A (en) * | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for an internal combustion engine |
| WO2003012263A1 (en) * | 2001-07-24 | 2003-02-13 | Robert Bosch Gmbh | Device for controlling gas exchange valves |
| WO2003016682A1 (en) * | 2001-08-08 | 2003-02-27 | Robert Bosch Gmbh | Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program and control and regulating device for operating an internal combustion engine |
| FR2869946A1 (en) * | 2004-05-06 | 2005-11-11 | Bosch Gmbh Robert | Hydraulic actuator for gas exchange valve of internal combustion engine, has hydraulic jack with chamber whose hydraulic liquid is evacuated by return conduit with less static pressure, where chamber is kept under low pressure |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19953789A1 (en) * | 1999-11-09 | 2001-05-10 | Bosch Gmbh Robert | Hydraulic gas exchange valve with a pressure adjuster arrangement for internal combustion engines |
| JP3776300B2 (en) | 2000-09-11 | 2006-05-17 | 本田技研工業株式会社 | Fuel cell stack |
| DE10147305A1 (en) | 2001-09-26 | 2003-04-17 | Bosch Gmbh Robert | Internal combustion engine |
| DE102004040210A1 (en) * | 2004-08-19 | 2006-03-02 | Robert Bosch Gmbh | Hydraulic controller for gas shuttle valve in internal combustion engine has hydraulic subsystem having differential pressure sensor connected to control unit by signal line |
-
2009
- 2009-11-20 DE DE102009046943A patent/DE102009046943A1/en not_active Withdrawn
-
2010
- 2010-10-15 WO PCT/EP2010/006325 patent/WO2011060855A2/en active Application Filing
- 2010-10-15 CN CN201080061039.4A patent/CN102713173B/en not_active Expired - Fee Related
-
2012
- 2012-06-15 FI FI20125667A patent/FI126134B/en not_active IP Right Cessation
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0455937A1 (en) * | 1990-05-11 | 1991-11-13 | Mitsubishi Jukogyo Kabushiki Kaisha | Valve driving apparatus of an internal combustion engine |
| US6148778A (en) * | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for an internal combustion engine |
| WO2003012263A1 (en) * | 2001-07-24 | 2003-02-13 | Robert Bosch Gmbh | Device for controlling gas exchange valves |
| WO2003016682A1 (en) * | 2001-08-08 | 2003-02-27 | Robert Bosch Gmbh | Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program and control and regulating device for operating an internal combustion engine |
| FR2869946A1 (en) * | 2004-05-06 | 2005-11-11 | Bosch Gmbh Robert | Hydraulic actuator for gas exchange valve of internal combustion engine, has hydraulic jack with chamber whose hydraulic liquid is evacuated by return conduit with less static pressure, where chamber is kept under low pressure |
Also Published As
| Publication number | Publication date |
|---|---|
| FI20125667A (en) | 2012-06-15 |
| CN102713173B (en) | 2015-06-17 |
| FI126134B (en) | 2016-07-15 |
| WO2011060855A3 (en) | 2011-07-14 |
| DE102009046943A1 (en) | 2011-05-26 |
| WO2011060855A2 (en) | 2011-05-26 |
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