CN102713173B - Electrohydraulic actuator - Google Patents
Electrohydraulic actuator Download PDFInfo
- Publication number
- CN102713173B CN102713173B CN201080061039.4A CN201080061039A CN102713173B CN 102713173 B CN102713173 B CN 102713173B CN 201080061039 A CN201080061039 A CN 201080061039A CN 102713173 B CN102713173 B CN 102713173B
- Authority
- CN
- China
- Prior art keywords
- control valve
- high pressure
- pressure control
- piston
- working room
- 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.)
- Expired - Fee Related
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
-
- 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 electrohydraulic actuator.
Background technique
The electrohydraulic actuator of the known scavenging air valve for controlling combustion engine have a clutch release slave cylinder, piston with first piston face and second piston area larger than first piston face that can move axially in clutch release slave cylinder, two that form in clutch release slave cylinder, by the working room of piston area gauge, and electrically operated valve.At this, the first piston of piston is in the face of a first working room's gauge being for good and all loaded the fluid be under high pressure and second working room's gauge of being connected with control valve one of the second piston area.The control valve being configured to solenoid valve selectively sets up the second working room and the fluid be under high pressure and the connection with the fluid be under low pressure.If the second working room is loaded the fluid be under high pressure, so piston moves out from its upper dead center position and causes opening of scavenging air valve.If the second working room is cut off relative to high pressure and low pressure, so piston to remain in its current stroke position and this scavenging air valve remains in its current open position thus.If the second working room is by off-load, the high pressure be so in the first working room causes piston to get back to backhaul in its upper dead center position, and scavenging air valve is closed again thus.
Summary of the invention
According to the present invention, propose a kind of electrohydraulic actuator, comprising: a clutch release slave cylinder; A piston that can move axially in this clutch release slave cylinder, this piston has first piston face and second piston area larger than this first piston face; Two working rooms formed in this clutch release slave cylinder, the first working room of one in these working rooms for good and all place's of being loaded fluid under high pressure by this first piston face gauge and second working room by this second piston area gauge; With the control valve of the electricity be connected in this second working room, these control valves are set up and the fluid located under high pressure and the connection locating fluid under low pressure alternatively, wherein, at least one in the connection of described second working room and high pressure and low pressure connects to be set up by multiple control valve, wherein, the connection of described second working room and high pressure is set up by multiple high pressure control valve, and wherein, described multiple high pressure control valve is connected with identical high-voltage power supply.
Especially obvious advantage is brought at it for during scavenging air valve in controlling combustion engine according to the electrohydraulic actuator of technique scheme feature of the present invention.By multiple preferably there is identical or different flow cross section and can be personalized such as time synchronization and/or time to stagger controlled control valve, allow the stroke of control piston very delicately and on purpose the lift curve of scavenging air valve exerted one's influence thus.By multiple high pressure control valve with identical or different flow cross section, allow to control these high pressure control valves than the little stroke by a unique high pressure control valve much better ground regulating piston by personalization, this unique high pressure control valve must have one for opening the very large flow cross section of stroke fast.Because the stroke of scavenging air valve correspond to piston open stroke during by the Fluid Volume of dosage, so the less Fluid Volume of scavenging air valve and stroke less thus can be regulated better than by a unique high pressure control valve with corresponding large flow cross section in the mode of execution of high pressure control valve with different flowings or through flow cross section.By the closedown postponed in time of high pressure control valve, the end of the opening procedure of scavenging air valve is not suddenly to be undertaken by approaching of continuing by conversion time of high dynamic control valve.Thereby reduce the overshoot tendency of scavenging air valve.Allow the maximum stroke very accurately regulating scavenging air valve thus.Different from the known technology of the overshoot for avoiding scavenging air valve, achieve the obvious more accurate dosage of the convection current scale of construction, produce the more accurate stroke precision of electrohydraulic actuator thus.
By multiple low-pressure control valve with identical or different flow cross section, allow the backhaul of much sensitive ground control piston and affect the trend of lift curve in stub area of scavenging air valve accurately.The scavenging air valve break of hydraulic pressure, it avoids valve cell to the hard collision of valve seat, also allows to realize very simply by multiple low-pressure control valve.
Favourable expansion scheme and the improvement project of the actuator in technique scheme can be realized by the measure listed in described below.
According to a kind of favourable mode of execution of the present invention, at least one high pressure control valve in described multiple high pressure control valve input side be connected to guide high pressure pressure duct on and at least one high pressure control valve be connected on a discharge aperture be passed in described first working room at input side.Described discharge aperture is arranged in described clutch release slave cylinder in this wise, makes described piston from a closed described discharge aperture by loading mobile stroke that trigger, that determine to the high pressure of described second working room of piston.Being connected to and correspondingly being inputted de-coupling thus with the fluid leading to the second working room by the corresponding high pressure control valve on the discharge aperture that crosses, the input of the Fluid Volume by hierarchically reducing can hierarchically be delayed and the mobile distance of accurately regulating piston.Effective stroke gauge can be realized thus and can be realized having the classification stroke of the step determined by suitable control.
According to a kind of favourable mode of execution of the present invention, at least one low-pressure control valve in described multiple low-pressure control valve to be connected with described second working room and at least one low-pressure control valve is connected on a discharge aperture be passed in described second working room at input side at input side.Described discharge aperture is arranged in described clutch release slave cylinder in this wise, make described piston from one by the high pressure unloading of described second working room is triggered, closed described discharge aperture the backhaul determined.If piston does not also arrive this stroke position, the flow cross section sum of low-pressure control valve that so fluid can be opened by these from the discharge of the second working room is carried out.Along with each in these discharge apertures is crossed, be cut off by the discharge being connected to the low-pressure control valve on discharge aperture and discharge by means of only remainder, the flow cross section that is reduced carries out.Discharge thus increasingly by throttling, in the second working room, form back pressure thus, this back pressure carries out throttling to the stroke speed of piston.Affect the stub area of the lift curve of scavenging air valve by low-pressure control valve permission thus and realize valve braking in a straightforward manner, the braking of this valve avoids valve cell firmly to strike on valve seat when valve cuts out fast.
Accompanying drawing explanation
The present invention is set forth in the following description in detail according to embodiment illustrated in the accompanying drawings.It illustrates with schematic diagram respectively:
Fig. 1 to 4 illustrates the longitudinal section for the electrohydraulic actuator be connected with the scavenging air valve of internal-combustion engine respectively with four embodiments altogether.
Embodiment
The cylinder cap 11 of deflagrating jar is partly shown with longitudinal section in Fig. 1 to 4, and this deflagrating jar surrounds a firing chamber 12 together with a reciprocating piston be directed in deflagrating jar.In cylinder cap 11, be configured with a gas channel 13 passed in firing chamber 12, the opening that passes into of this gas channel is controlled by a scavenging air valve 14.Scavenging air valve 14 can be entrance or outlet valve.Scavenging air valve 14 comprises one and is arranged in seat ring 15 in cylinder cap 11 and a valve cell 18 having valve rod 19 and be arranged in the valve disc 20 on valve rod 19 end, the valve seat 17 of valve opening 16 and encirclement valve opening 16 is configured in this seat ring, and this valve disc and valve seat 17 acting in conjunction are to discharge and draught excluder opening 16.
The valve cell 18 of scavenging air valve 14 operates by electrohydraulic actuator 21.Actuator 21 have that 23, two, piston that a clutch release slave cylinder 22, axially movably can be directed in clutch release slave cylinder 22 is formed in clutch release slave cylinder 22, by the working room 24,25 of piston 23 gauge and electrically operated valve.Piston 23 with first piston face 231 to the first working room 24 gauge and with second piston area 232 larger than this piston area 231 to the second working room 25 gauge.First working room 24 is the place's of being loaded fluid under high pressure for good and all, and these control valves are connected in the second working room 25 and set up alternatively and place's fluid under high pressure and the connection locating fluid under low pressure.
In order to provide fluid high-pressure and low pressure, be provided with a fluid storage 26, high-pressure service pump 27, pressure duct 28 and an offloading pipeline 29.This high-pressure service pump 27 is from fluid storage 26 pumping fluid and by fluid storage under high pressure in pressure duct 28.The fluid of discharging from the second working room 25 is transmitted back in fluid storage 26 by low pressure or offloading pipeline 29.Such as, the low pressure in offloading pipeline 29 is between 1 to 6 bar.High pressure in the second working room 25 with pressure duct 28 and with the connection of the low pressure in offloading pipeline 29 (being set up by control valve in all embodiments of their electrohydraulic actuator 21 in Fig. 1 to 4), these connect at least one set up by multiple control valve.In the embodiment in figure 1, the second working room 25 is set up by multiple high pressure control valve with the connection of high pressure, and two high pressure control valves 30,31 in these high pressure control valves are shown to citing in FIG.The connection of the second working room 25 and low pressure is undertaken by a unique low-pressure control valve 32.Multiple, these two high pressure control valves 30,31 input side be connected in parallel guide high pressure pressure duct 28 on.Multiple high pressure control valve 30,31 not only can have identical flow cross section but also can have different flow cross sections and personalized ground, such as to be controlled with synchronously or in time staggering in time.The electric control of all control valves (it is such as configured to two-position two-way solenoid valve at this) is by carrying out at this unshowned motor control assembly.
If low-pressure control valve 32 is controlled and to be closed thus and high pressure control valve 30,31 is controlled and is opened thus, the large fluid volume be so under high pressure flow in the second working room 25.Piston 23 to move and scavenging air valve 14 is opened rapidly dead center position from it with high speed, thus the lift curve of this scavenging air valve has precipitous input side edge.If stroke of piston period one of two high pressure control valves 30,31 be closed, the Fluid Volume flowed into so again in the second working room 25 obviously reduces.Velocity of piston declines, and the mobile distance of piston 23 can be accurate many ground is controlled.Meanwhile, piston 23 can be controlled very exactly and the overshoot of piston 23 is reduced significantly by the unexpected closedown of the high pressure control valve 30 or 31 retained to sailing in the strokes ends position of wishing (this strokes ends position corresponds to the opening of determination of scavenging air valve).The overshoot tendency of valve cell 18 in the open position determined of scavenging air valve 14 is reduced thus.
The embodiment of the electrohydraulic actuator 21 in Fig. 2 is modified relative to electrohydraulic actuator in FIG, namely high pressure control valve 31 is free of attachment on fluid circuit 28 at input side, but is connected on a discharge aperture 34 be passed in the length of stroke of piston 23 in first working room 24.Thus in multiple high pressure control valve (citing ground illustrates two control valves 30,31 wherein in fig. 2), at least one high pressure control valve to be connected on the pressure duct 28 of guiding high pressure and at least one high pressure control valve is connected on discharge aperture 34 at input side at input side.At this, multiple discharge aperture 34 can be passed in the second working room 25 and to be connected with the input end of other high pressure control valve respectively, and the output terminal of these other high pressure control valves is connected to again in the second working room 25.Discharge aperture 34 is arranged in clutch release slave cylinder 22, namely this discharge aperture determine from one, by the high pressure of the second working room 25 being loaded to being closed by piston 23 from upper dead center position mobile stroke out of triggering.This position (wherein discharge aperture 34 is closed) of piston 23 marks in fig. 2 dotted line and represents by 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, so piston 23 can maximally move in stroke position 35.What can realize piston 23 by multiple discharge aperture (discharge aperture 34 wherein shown in Figure 4) thus has the classification stroke determining step.Additionally, can by the stroke characteristic to the control effect piston 23 of the suitable personalization of high pressure control valve 30,31.
According in the electrohydraulic actuator 21 of Fig. 3, eliminate the addition thereto for affecting piston 23 when moving out from the upper dead center position of piston, thus the second working room 25 is connected on pressure duct 28 with the large flow cross section needed for a motion of the fast moving for piston 23 by a unique high pressure control valve 30.On the contrary, the second working room 25 is set up by multiple low-pressure control valve with the connection of the offloading pipeline 29 guiding low pressure, and two low pressure valves 32,33 are wherein shown to citing in figure 3.In multiple low-pressure control valve 32,33, at least one low-pressure control valve (in this case low-pressure control valve 32) is connected with the second working room 25 at input side, and at least one low-pressure control valve (in this case low-pressure control valve 33) is connected on a discharge aperture 34 be passed in the stroke range of piston 23 in second working room 25 at input side.Discharge aperture 34 is arranged in clutch release slave cylinder 22, makes piston 23 closed discharge aperture from the backhaul triggered by the high pressure unloading of the second working room 25 determined.The stroke position (discharge aperture 37 is closed from this stroke position) of piston 23 is illustrated in figure 3 dotted line and represents with 38.Low-pressure control valve 32,33 can have identical flow cross section, but also can be provided with different flow cross sections.Personalization ground, such as time synchronization or time are controlled low-pressure control valve 32,33 with staggering again.Also can be connected with each discharge aperture at input side at this other low-pressure control valve 32,33, these discharge apertures are upper and lower in clutch release slave cylinder to be arranged stackedly, and piston 23 is enclosed in the discharge aperture 37 of successive in length of stroke successively thus.
If high pressure control valve 30 is closed and two low-pressure control valves 32,33 are opened, so in the backhaul of piston 23, fluid is undertaken from the discharge of the second working room 25 by two low-pressure control valves 32.Large discharge cross section is obtained by the flow cross section sum of low-pressure control valve 32,33 and piston 23 quickly back moves, and scavenging air valve 14 is closed thus rapidly.If piston 23 arrives stroke position 38, so discharge aperture 37 is ended by piston 23.Fluid is only discharged by the flow cross section obviously less than cross section sum of low-pressure control valve 32.This discharge obviously more consumingly by throttling, build-up pressure and throttling is carried out to the speed of closing movement in the second working room 25 thus.Low-pressure control valve 32 may be used for the braking of control piston 23 and causes the closedown of scavenging air valve 14 thus, and wherein valve disc 20 is not firmly impact on valve seat 17.When last low-pressure control valve 32 is initiatively constructed to Proportional valve, obtain the other control possibility in the backhaul stage of piston 23.
In the embodiment of electrohydraulic actuator 21 shown in Figure 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.Liang Ge working room 25 is undertaken by least two high pressure control valves 30,31 with the connection of high pressure, and a high pressure control valve in these high pressure control valves to be connected on pressure duct 28 and another high pressure control valve to be connected at input side on the discharge aperture 34 that to pass in the stroke path of piston 23 in first working room 24 at input side.At outlet side, two high pressure control valves 30,31 are connected with Liang Ge working room 25.Second working room 25 is undertaken by least two low-pressure control valves 32,33 with the connection of low pressure, and a low-pressure control valve in these low-pressure control valves to be connected in the second working room 25 and the second low-pressure control valve 33 is connected on the discharge aperture 37 that to be passed in the length of stroke of reciprocating piston 23 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 electrohydraulic actuator 21, the above-mentioned possibility for the lift curve affecting scavenging air valve provides with sum.In conversion, high pressure control valve 30,31 also can be connected as it as shown in Figure 1.
In described electrohydraulic actuator 21, the opening stroke and still can otherwise be affected, such as, by the annular piston that a seat is put on piston 23, as it describes in DE 101 43 952A1, Fig. 2 of piston 23.In addition, electrohydraulic actuator 21 also can a pair outlet valve of controlling combustion engine or a pair inlet valve, and to be the piston 23 that is configured to classification or stepped piston act on valve with one to its mode is connected upper coupling unit.So-called " double plate " such as describes in DE 101 47 305 A1.
Claims (11)
1. electrohydraulic actuator, comprising: a clutch release slave cylinder (22); A piston (23) that can move axially in this clutch release slave cylinder (22), this piston has first piston face (231) and second piston area (232) larger than this first piston face; Two working rooms (24 formed in this clutch release slave cylinder (22), 25) first working room (24) of one, in these working rooms for good and all place's of being loaded fluid under high pressure by this first piston face (231) gauge and second working room (25) by this second piston area (232) gauge; With the control valve of the electricity be connected in this second working room (25), these control valves are set up and the fluid located under high pressure and the connection locating fluid under low pressure alternatively, wherein, at least one in the connection of described second working room (25) and high pressure and low pressure connects to be set up by multiple control valve, it is characterized in that, the connection of described second working room (25) and high pressure is by multiple high pressure control valve (30,31) set up, wherein, described multiple high pressure control valve is connected with identical high-voltage power supply.
2. electrohydraulic actuator according to claim 1, is characterized in that, described second working room (25) is set up by multiple low-pressure control valve (32,33) with the connection of low pressure.
3. electrohydraulic actuator according to claim 1, is characterized in that, described multiple high pressure control valve (30,31) is connected on the pressure duct (28) of guiding high pressure in parallel at input side.
4. electrohydraulic actuator according to claim 2, is characterized in that, described multiple high pressure control valve (30,31) is connected on the pressure duct (28) of guiding high pressure in parallel at input side.
5. according to the electrohydraulic actuator of one of Claims 1-4, it is characterized in that, described multiple high pressure control valve (30, 31) at least one high pressure control valve (30) in is connected at input side and guides the pressure duct (28) of high pressure upper and at least one high pressure control valve (31) is connected to one in the scope of the length of stroke of described piston (23), is passed into that discharge aperture (34) in described first working room (24) is upper and described discharge aperture (34) is arranged in described clutch release slave cylinder (22) in this wise, described piston (23) is triggered from one by load the high pressure of described second working room (25), the mobile stroke determined starts closed described discharge aperture.
6. according to the electrohydraulic actuator of one of claim 2 to 4, it is characterized in that, described multiple low-pressure control valve (32, 33) at least one low-pressure control valve (32) in be connected with described second working room (25) and at least one low-pressure control valve (33) is connected to one at input side in the scope of the length of stroke of described piston (23), is passed into that discharge aperture (37) in described second working room (25) is upper and described discharge aperture (37) is arranged in described clutch release slave cylinder (22) in this wise at input side, make described piston (23) from one by trigger the high pressure unloading of described second working room (25), the backhaul determined starts closed described discharge aperture.
7. according to the electrohydraulic actuator of one of Claims 1-4, it is characterized in that, described multiple high pressure control valve (30,31) has different flow cross sections.
8. according to the electrohydraulic actuator of one of claim 2 to 4, it is characterized in that, described multiple low-pressure control valve (32,33) has different flow cross sections.
9. according to the electrohydraulic actuator of one of Claims 1-4, it is characterized in that, described multiple high pressure control valve (30,31) can be controlled individually.
10. according to the electrohydraulic actuator of one of claim 2 to 4, it is characterized in that, described multiple low-pressure control valve (32,33) can be controlled individually.
11. according to the electrohydraulic actuator of one of claim 2 to 4, it is characterized in that, described piston (23) is connected in this wise with the valve cell (18) of at least one scavenging air valve (14) of internal-combustion engine, make at described low-pressure control valve (32, 33) by described multiple high pressure control valve (30 when closing, 31) at least one open described at least one scavenging air valve (14) and at described multiple high pressure control valve (30, 31) at described low-pressure control valve (32 when closing, 33) described in when at least one in is opened, at least one scavenging air valve (14) is 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 CN102713173A (en) | 2012-10-03 |
| CN102713173B true 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 |
|---|---|---|---|---|
| US20130152572A1 (en) * | 2011-12-16 | 2013-06-20 | Jeffrey Madderno | Valve activation 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 (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6148778A (en) * | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for 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 (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2527268Y2 (en) * | 1990-05-11 | 1997-02-26 | 三菱重工業株式会社 | Valve train for internal combustion engine |
| 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 |
| DE10136020A1 (en) * | 2001-07-24 | 2003-02-13 | Bosch Gmbh Robert | Control device for IC engine gas changing valves has common electrically-operated control valves associated with each pair of hydraulic valve setting devices for respective gas changing valves |
| DE10138881A1 (en) * | 2001-08-08 | 2003-02-27 | Bosch Gmbh Robert | Method for operating an electro-hydraulic valve control of an internal combustion engine, computer program and control and regulating device for operating an internal combustion engine |
| 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 (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6148778A (en) * | 1995-05-17 | 2000-11-21 | Sturman Industries, Inc. | Air-fuel module adapted for 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 |
|---|---|
| WO2011060855A2 (en) | 2011-05-26 |
| CN102713173A (en) | 2012-10-03 |
| DE102009046943A1 (en) | 2011-05-26 |
| FI126134B (en) | 2016-07-15 |
| WO2011060855A3 (en) | 2011-07-14 |
| FI20125667A (en) | 2012-06-15 |
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