CN104169532A - A hydraulic valve arrangement for controllably operating a gas exchange valve of an internal combustion piston engine - Google Patents
A hydraulic valve arrangement for controllably operating a gas exchange valve of an internal combustion piston engine Download PDFInfo
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- CN104169532A CN104169532A CN201380009436.0A CN201380009436A CN104169532A CN 104169532 A CN104169532 A CN 104169532A CN 201380009436 A CN201380009436 A CN 201380009436A CN 104169532 A CN104169532 A CN 104169532A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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Abstract
Invention relates to a hydraulic valve arrangement (10) for controllably operating a gas exchange valve of an internal combustion piston engine, the arrangement comprising a body part (12) in which body part a first fluid chamber (14.1) is arranged bordered by radial surfaces (16.1', 16.2') of first and second piston parts and having a volume that increases in response to the piston parts (16.1, 16.2) moving relative to the body part in a first direction, and a second fluid chamber (14.2) is arranged bordered by radial surface (16.2'') of the second piston part having a volume that decreases in response to the second piston part moving relative to the body part in a first direction. The first and the second piston parts are arranged slidably in respect to each other and that the movement of the second piston (16.2) part relative to the body part (12) is arranged controllable by a fluid control system (24) arranged in connection with the hydraulic valve arrangement (10).
Description
Technical field
The present invention relates to a kind of for controllably operating the fluid pressure valve device of gas exchange valve of internal combustion piston engine, this device comprises main body, this main body has the working space for placement operations piston, this operated piston at least comprises concentric first piston part and the second piston portion, and in this main body, first-class body cavity is arranged to the radial surface limited boundary by first piston part and the second piston portion, and the volume of this first-class body cavity in response to these piston portions with respect to movement in a first direction of main body and increase, and second body cavity is arranged to the radial surface limited boundary by the second piston portion, and the volume of this second body cavity in response to the second piston portion with respect to main body moving and reducing in a first direction.
Background technique
Explosive motor generally includes multiple gas exchange valves.These valve controls are by the inlet and outlet of the air-flow of the firing chamber of motor.Typical motor will comprise at least one suction valve and at least one gas outlet valve for each cylinder or each firing chamber of motor.Each valve open the predetermined cam or the crankshaft angular place that are timed in the operation cycle that occurs in motor.Well-known, the advantage in control time is, in the time of engine running, the gas exchange valve of motor is opened.In the time that for example running speed is higher and while needing maximum capacity, the time that the maximum capacity of motor can be opened by prolongation valve plays a role.And available engine torque can be for example by selecting suitable opening time to increase in the time of partial load and slow speed for valve.By carry out the best opening time of modulating valve according to its operator scheme during each stroke of motor, can reduce consumption and the noxious emission of fuel.
The starting of this adjustable valve can realize by hydrovalve operation system.As an example of this system, EP140347381B1 discloses a kind of actuating assembly, and this actuating assembly has: main body; Valve, this valve moves the piston of slidably arranging with respect to this main body; And first, second, and third hydraulic pressure cavity, these hydraulic pressure cavity are limited between described piston and described main body, wherein, described the first chamber and described the second chamber have the volume reducing in response to the piston moving in a first direction with respect to described main body, and described the 3rd chamber has the volume increasing in response to the piston moving in a first direction with respect to described main body.
US2004055547A1 shows a kind of hydraulic actuator, wherein, carrys out as follows design operation piston, that is: the region surface of at least one effective area in two effective areas is along the sliding path of operated piston and change.Particularly, it shows a kind of device, and wherein, piston has multiple parts and has two local pistons, and these two local pistons have different axial lengths and they are concentrically inserted into inside each other, to can move relative to each other.Therefore, by the effective area of the combination of concentric piston, gas exchange valve can promptly be opened under the effect of large displacement force, and then this displacement force promptly declines and keep constant on the remainder only lifting by inner carrier of valve.
Hydraulic actuator for controlling and the opening and closing of modulating valve provide possibility widely during operation motor.But, due to the quite high flow velocity of hydraulic fluid, so the challenge that hydraulic pressure gas exchange valve activates is energy efficiency.
The object of the present invention is to provide a kind ofly for controllably operating the fluid pressure valve device of gas exchange valve of internal combustion piston engine, this internal combustion piston engine provides controllability and minimum energy consumption flexibly.
Summary of the invention
Object of the present invention realizes by a kind of fluid pressure valve device for the gas exchange valve that controllably operates internal combustion piston engine substantially, this fluid pressure valve device comprises main body, this main body has the working space for placement operations piston, this operated piston at least comprises the first and second piston portions of relative to each other slidably arranging with one heart, and in described main body, first-class body cavity is arranged to by both radial surface limited boundaries of described the first and second piston portions, and the volume of this first-class body cavity in response to these piston portions with respect to the movement in a first direction of described main body and increase, and second body cavity is arranged to the radial surface limited boundary by described the second piston portion, and the volume of this second body cavity in response to described the second piston portion with respect to described main body moving and reducing in a first direction.The invention is characterized in, described the second piston portion is arranged to be independent of described first piston part with respect to the motion in a first direction of described main body and can be controlled by liquid control system, and this liquid control system is arranged to be connected with described fluid pressure valve device.
Like this, can be by thering is the hydraulic fluid of optimum flow rate with respect to complete the work that regulates described device for the required power of mobile piston on described first direction.
According to an embodiment of the present invention, described liquid control system comprises pressure line, this pressure line is connected to source of pressurised fluid and described first-class body cavity and is provided with pressure valve, and each fluid chamber is communicated with controlled mode fluid with described pressure line, wherein the volume of each fluid chamber in response at least one piston portion in described piston portion with respect to described main body moving and reducing in a first direction.
According to an embodiment of the present invention, described liquid control system comprises fluid line, and this fluid line is connected to described second body cavity the low-pressure section of described liquid control system in controlled mode.
According to an embodiment of the present invention, the 3rd fluid chamber is arranged to the radial surface limited boundary by least described first piston part, and the volume of the 3rd fluid chamber in response to described first piston part relative to described main body moving and reducing in a first direction.Described first-class body cavity and described the 3rd fluid chamber can optionally be connected to pressurized hydraulic fluid source.
According to an embodiment of the present invention, the described radial surface on the border of the described first-class body cavity of restriction of described first piston part is less than the radial surface on the border of described the 3rd fluid chamber of restriction of described first piston part, and the described radial surface on the border of described the 3rd fluid chamber of the restriction of described first piston part is less than the described radial surface on the border of the described second body cavity of restriction of described the second piston portion.
According to an embodiment of the present invention, described first piston part is arranged to freely to move in a first direction with respect to described the second piston portion, and this first piston part is provided with mechanical stopping piece, this mechanical stopping piece limits the motion of described the second piston portion with respect to described first piston part.
Brief description of the drawings
Below, with reference to exemplary schematic figures, the present invention is described, wherein
Fig. 1 shows the fluid pressure valve device for controllably operating the gas exchange valve of internal combustion piston engine according to an embodiment of the present invention;
Fig. 2 shows for controllably operating according to the fluid pressure valve device of the gas exchange valve of the internal combustion piston engine of another embodiment of the present invention; And
Fig. 3 shows for controllably operating according to the fluid pressure valve device of the gas exchange valve of the internal combustion piston engine of a mode of execution more of the present invention.
Embodiment
In Fig. 1, schematically show the fluid pressure valve device 10 for internal combustion piston engine according to an embodiment of the present invention.
By this fluid pressure valve device, can be with the operation except the timing in its cycle period with respect to piston and open and/or closed ramp (ramp) of mode control valve very flexibly.This device comprises main body 12, is furnished with working space 14 in this main body.This device also comprises operated piston 16, and this operated piston is disposed in working space.The mode that this operated piston transmits with power is connected with the gas exchange valve 18 of motor.Operating valve 16 is arranged in working space 14, to move, thereby thereby it can be moved in a first direction causes opening motion and can correspondingly moving up and cause the closing movement of gas exchange valve 18 in the second party contrary with first direction of gas exchange valve 18.Working space 14 is arranged in rotational symmetric mode with respect to its central axis 20.This working space extends at one end thereof place and becomes guide section 22, and this guide section has the internal diameter of selecting corresponding to the external diameter of operated piston 16 at respective regions, thereby realizes the desired guiding effect of piston 16.
Operated piston 16 at least comprises concentric first piston part 16.1 and the second piston portion 16.2.Described first piston part 16.1 and the second piston portion 16.2 are arranged to relative to each other to slide, and the second piston portion 16.2 is delimited by the mechanical stopping piece 50 that is arranged into first piston part 16.1 with respect to the motion of first piston part in a first direction.Also have the second mechanical stopping piece 51 that is arranged into main body 12, this second mechanical stopping piece cooperates with the second piston portion 16.2.The movement limit of the second piston portion 16.2 in second direction arrived the precalculated position with respect to main body 12 by this second retainer.This second retainer defines the initial position of the second piston portion 16.2.These piston portions are arranged to be controlled by liquid control system 24, and this liquid control system is arranged in the mode being connected with fluid pressure valve device.
Figure 2 illustrates and the identical control valve unit 10 shown in above-mentioned Fig. 1, but this control valve unit can be by allowing the liquid control system 24 that control valve unit is carried out to more complicated control to control.
During operation is according to the fluid pressure valve device of an embodiment of the present invention shown in Fig. 1 and Fig. 2, the second piston portion 16.2 helps first piston part 16.1 motion in a first direction in the time that valve 18 is opened.During the fold return motion of operated piston, the second piston portion is back into its initial position against the second mechanical stopping piece 51 by first piston part 16.1.
In main body 12, in working space, there is first-class body cavity 14.1, this first-class body cavity 14.1 is arranged to partly radial surface 16.1 ', the 16.2 ' limited boundary by first piston part 16.1 and both first end places that is positioned at them of the second piston portion 16.2, and the volume of this first-class body cavity is in response to any one or both in these piston portions 16.1,16.2 movements on first direction (that is: in Fig. 1 and Fig. 2 downward direction) and increasing with respect to main body 14.This working space also comprises second body cavity 14.2, this second body cavity 14.2 is arranged to partly the radial surface that is positioned at its second end place 16.2 by the second piston portion in working space " limited boundary, and the volume of this second body cavity in response to the second piston portion with respect to main body moving and reducing on first direction (that is: in Fig. 1 and Fig. 2 downward direction).
As depicted in figs. 1 and 2, radial surface 16.1 ', 16.2 ', 16.2 " limit as follows useful area; make in the arranged in form against with shoulder during to the mechanical stopping piece 50 of first piston part; 16.1 ' limits the area of the first end of first piston part 16.1; 16.2 ' limits the area of the first end of the second piston portion 16.2, and 16.2 " limit the area of the second end of the second piston portion.
Liquid control system 24 comprises the pressure line 26 that is connected to source of pressurised fluid 28 and is also connected to first-class body cavity 14.1, and is provided with pressure valve 30.Therefore, can allow that pressure fluid enters chamber 14.1 and makes piston portion 16.1 and 16.2 stressed in controlled mode.Now, the second piston portion 16.2 is arranged to be controlled by liquid control system 24 with respect to the motion of main body 12, make second body cavity 14.2 be communicated with 34 with controlled fluid and be communicated with the low-pressure section 36 of liquid control system, wherein the volume of this second body cavity in response to the second piston portion 16.2 relative to main body moving and reduce in a first direction.Like this, the motion of the second piston portion 16.2 is arranged to be independently controlled in liquid control system 24.More particularly, this liquid control system 24 comprises fluid line 38, and this fluid line has valve 40, and this valve is connected to low-pressure section 36 in controlled mode by second body cavity 14.2.By the valve 40 in this fluid line, can control fluid flowing from second body cavity 14.2.The fluid flowing out from the second chamber defines the mobile status of the second piston portion 16.2.Therefore, if while stoping fluid to flow out second body cavity 14.2, even if valve 30 is opened, the second piston portion 16.2 also can not move.In the case, only have piston portion 16.1 to move and piston portion 16.2 remains essentially in its current location, this current location represents position when valve 30 cuts out.Valve 30 can be controlled as and cutting out in any suitable moment between 16 moving periods of piston, makes the motion of the second piston portion 16.2 only move to desired degree along first piston part 16.1.
As shown in Figure 2, according to an embodiment of the present invention, second body cavity 14.2 is communicated with 32 with controlled fluid in addition and is communicated with first-class body cavity 14.1.In the mode of execution of Fig. 2, this is achieved by the controlled fluid connection 32 being communicated with the pressure line 26 that is positioned at pressure valve 30 downstreams, and this controlled fluid is communicated with (32) and has valve 31.Like this, can make pressure fluid act on the two ends of the second piston portion 16.2.Because the radial surface 16.2 ' that is positioned at the first end place of the second piston portion in the original position shown in Fig. 2 is greater than the radial surface 16.2 at the second end place that is positioned at the second piston portion ", so the power that is applied to first piston part 16.1 by the second piston portion 16.2 is by surface area 16.2 ' and 16.2 " difference limit.Therefore, the effect of the second piston portion 16.2 is by opening from second body cavity 14.2 to pressure line or the fluid flow communication of the low-pressure section 36 of system or control by closing from the fluid flow communication of second body cavity 14.2.Open and control valve 40 is closed and hydraulic fluid is fed into first-class body cavity 14.1 in the situation that, hydraulic fluid turns back to pressure line 26 from second body cavity 14.2, and therefore less from the required flow in pressurized hydraulic fluid source at control valve 31.Therefore, the second piston portion stops being arranged to be independent of first piston part with respect to main body motion in a first direction.This also means that the process that power is delivered to first piston part from the second piston portion stops.This feature is presented in institute's drawings attached 1 to 3.
Working space 14 and first piston part 16.1 limit the 3rd fluid chamber 14.3, the 3rd fluid chamber is arranged to partly by the radial surface 16.1 of first piston part 16.1 at least " limited boundary, and the volume of the 3rd fluid chamber in response to first piston part with respect to main body moving and reducing in a first direction.The 3rd fluid chamber can be to be optionally connected to source of pressurised fluid 28 by the fluid line 46 with valve 42, this source of pressurised fluid is convenient to piston in the upper motion of second direction (direction that, gas exchange valve 18 is moved on its closing direction).Pressure line (, the first chamber 14.1) also can optionally be connected to by the fluid line with valve 62 low-pressure section 36 of system.
As shown in Figure 2, the 3rd fluid chamber 14.3 also can be communicated with first-class body cavity 14.1 with controlled fluid connection 44.In the mode of execution of Fig. 2, this is achieved by the controlled fluid connection 44 being communicated with the pressure line 26 that is positioned at pressure valve 30 downstreams, and this controlled fluid is communicated with (44) and has valve 43.Like this, can make pressurized hydraulic fluid act on the first end of first piston part 16.1 with and radial surface 16.1 " on.Because be greater than the radial surface 16.1 on the border that limits the 3rd chamber at the radial surface 16.1 ' at the first end place of first piston part "; so in the time opening from the 3rd chamber to the connection of pressure line 26, the power that is applied to first piston part 16.1 is limited by the difference of surface area.Therefore, the effect of first piston part 16.1 is controlled by the fluid flow communication of opening the low-pressure section 36 from the 3rd fluid chamber 14.3 to pressure line or system.The 3rd chamber 14.3 is connected to low-pressure section 36 by the circuit 46 that is provided with control valve 48.In addition, the second chamber 14.2 is connected to low-pressure section 36 by the circuit 38 that is provided with control valve 40 in controlled mode.
Preferably, each fluid chamber with controlled fluid be communicated with the downstream that is positioned at pressure valve (, be positioned at a side place of first-class body cavity) pressure line be connected, wherein the volume of each fluid chamber in response at least one piston portion in piston portion relative to main body moving and reducing in a first direction.
Because the device in Fig. 1 and Fig. 2 comprises two piston portions, so can apply in different power to piston 16 in some combinations of the control valve by suitably opening and closing, select the mode of the useful area that utilizes them.In practice, the advantage of this device is to have optional useful area, that is, and and the combined radial surface in working space 14.Like this, according to for example engine load, motor robot device can be selected used useful area.In the time selecting useful area to make to be equated with restraint by the power of hydraulic pressure generation, required flow of pressurized is minimized, thus energy saving.If this useful area is greater than the required area of these power, the also large and extra energy of system consumption of required flow of pressurized, this extra energy will be minimized by the present invention.
As the example of the work of a control valve unit, oil hydraulic cylinder has at least three fluid chambers 14.1,14.2,14.3.Chamber 14.1 on top in Fig. 1 and Fig. 2 is for pressing down piston 16, and this motion will be opened gas exchange valve 18.The 3rd chamber 14.3 in accompanying drawing is also for upwards pushing this piston, and this will close gas exchange valve.The second chamber is that intermediate cavity 14.2 is for controlling volume.
If the control valve 40 in this second chamber 14.2 is closed, the hydraulic fluid (for example: oil) in the second chamber 14.2 is tending towards moving down Shi Buhui outflow at inner carrier.Therefore the second piston portion 16.2 can not move, and therefore, unique part of carrying out this operation is first piston part 16.1.If the power obtaining is in this way enough, the flow of required fluid is less.In the case, the power producing is the hydraulic pressure of the surface area 16.1 ' in chamber 14.1.The volume in the 3rd chamber 14.3 is connected to low-pressure section 36 (container).For example, if need larger power (engine load maximum), open the control valve 40 of the second volume 14.2, thereby the second volume 14.2 is connected to low-pressure section 36, and two pistons move down, thereby outer piston part 16.2 is pushed inner carrier part 16.1.Now obtain effective force by the piston area 16.1 ' and 16.2 ' of combination.This system can be provided with plural piston portion and radial surface.
Advantage of the present invention is also, even also can change applied force during the stroke of piston, that is, changes useful area, and this makes the operation of fluid pressure valve device more energy-conservation.
The 3rd chamber 14.3 turns back to while opening one's mouth position pressurized at piston.Now, the first chamber 14.1 is connected to low-pressure section 36 (container).According to an embodiment of the present invention, valve 31 is also opened.This can reach following object, that is, make can flow to low-pressure section 36 by valve 62 or valve 40 (or both) from the fluid in two chambeies 14.1 and 14.2.Like this, even if the arbitrary valve in valve 62 or valve 40 is not worked, piston 16 still can return to its initial position.As a rule, the first chamber 14.1 is connected low-pressure section 36 with the second chamber 14.2 in optional mode and/or in controlled mode, selects because can realize operation by control valve 31.
Gas exchange valve return need to be less power, this is because there is not the engine pressure of constrained motion.Therefore, cause the area of this return movement to be less than and cause the area of motion in a first direction.
Device in Fig. 1 and Fig. 2 allows for each load condition, the useful area of actuator to be regulated.
In following form, illustrate that the possible power that can be obtained by the device with predetermined pressure in Fig. 1 and Fig. 2 combines.
| Useful area | Valve 30 | Valve 40 | Valve 48 | Valve 31 | Valve 43 |
| 16.1’ | Open | Close | Open | Close | Close |
| 16.1’+16.2’ | Open | Open | Open | Close | Close |
| 16.1’+16.2’-16.2” | Open | Close | Open | Open | Close |
| 16.1’+16.2’-16.1” | Open | Open | Close | Close | Open |
| 16.1’+16.2’-16.2”-16.1” | Open | Close | Close | Open | Open |
The useful area of these alternatives is for piston 16 motion in a first direction, thereby allows, under identical stress level, seven different power are applied to piston.In all combinations, valve 30 is all opened.Available power depends on these areas and the actual size of the hydraulic pressure that adopts.
In Fig. 2, also show accumulator system 55, this accumulator system 55 can optionally be connected to pressure line 26 and the circuit 46 being connected with the low-pressure section 36 of system by valve 56 and 57.By using this accumulator system and valve, the motion of piston 16 can be slowed down, thereby also makes the recycling of energy become possibility.
Figure 3 illustrates another embodiment of the present invention, be wherein furnished with three piston portions in coaxial mode, that is: first piston part 16.1, the second piston portion 16.2 and the 3rd piston portion 16.3.In Fig. 3, adopt corresponding reference character for respective element in Fig. 1 and Fig. 2.Each fluid chamber 14.2,14.3 and 14.4 is communicated with the pressure line 26 in the downstream that is positioned at pressure valve with the controlled fluid connection with control valve 29,31,43, and each fluid chamber all has the volume reducing in response at least one piston portion moving in a first direction relative to main body.In the mode of execution of Fig. 3, liquid control system 24 comprises fluid line 23, and this fluid line has valve 25, and this valve is also connected to low-pressure section 36 in controlled mode by the 4th fluid chamber 14.4.
Interior coaxial piston part and outer coaxial piston part are also arranged such that the motion of outer coaxial piston part is limited to predetermined lengthwise position with respect to interior coaxial piston part.Preferably the motion of this outer coaxial piston part is limited with the relative surperficial form of outer coaxial piston part by interior coaxial piston part.
This device can be provided with spring element 60, and this spring element promotes piston so that in for example moving to the 3rd fluid chamber along second direction.
Although by example, in conjunction with being considered to most preferred mode of execution at present, invention has been described here, but be understood that, the present invention is not limited to published mode of execution, but as defined in the appended claims, be intended to cover it and comprise feature within the scope of the present invention and various combination or the modification of some other application.All can use in conjunction with another mode of execution in conjunction with the details described in arbitrary mode of execution above, it is feasible being combined in technical if such.
Claims (10)
1. one kind for controllably operating the fluid pressure valve device (10) of gas exchange valve of internal combustion piston engine, this fluid pressure valve device comprises main body (12), this main body has the working space (14) for placement operations piston (16), this operated piston at least comprises first piston part (16.1) and the second piston portion (16.2) relative to each other slidably arranged with one heart, and in described main body, first-class body cavity (14.1) is arranged to the radial surface (16.1 ' by described first piston part and described the second piston portion, 16.2 ') limited boundary, and the volume of this first-class body cavity is in response to these piston portions (16.1,16.2) with respect to the movement in a first direction of described main body and increase, and second body cavity (14.2) is arranged to by the radial surface of described the second piston portion (16.2 ") limited boundary, and the volume of this second body cavity in response to described the second piston portion with respect to described main body moving and reducing in a first direction, it is characterized in that, described the second piston portion (16.2) is arranged to be independent of described first piston part (16.1) and can be controlled by liquid control system (24) with respect to described main body (12) motion in a first direction, this liquid control system is arranged to be connected with described fluid pressure valve device (10).
According to claim 1 for the described fluid pressure valve device (10) of operating gas crossover valve controllably, it is characterized in that, described liquid control system comprises pressure line (26), this pressure line is connected to source of pressurised fluid (28) and described first-class body cavity (14.1) and is provided with pressure valve (30), and each fluid chamber (14.2 ', 14.3 ', 14.4 ') be all communicated with controlled mode fluid with described pressure line (26), wherein the volume of each fluid chamber is in response to these piston portions (16.1, 16.2, 16.3) at least one piston portion in is with respect to described main body moving and reducing in a first direction.
3. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described liquid control system (24) comprises fluid line (38), this fluid line (38) comprises valve (40), and this valve (40) is connected to described second body cavity (14.2) low-pressure section (36) of described liquid control system in controlled mode.
4. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described fluid pressure valve device comprises the 3rd fluid chamber (14.3), the 3rd fluid chamber is arranged to the radial surface limited boundary by least described first piston part (16.1 "), and the volume of the 3rd fluid chamber in response to described first piston part relative to described main body moving and reducing in a first direction, and described first-class body cavity can optionally be connected (30 with described the 3rd fluid chamber, 42) to pressurized hydraulic fluid source (28).
5. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, the described radial surface (16.1 ') on the border of the described first-class body cavity of restriction (14.1) of described first piston part (16.1) is less than the radial surface (16.1 ") on the border of described the 3rd fluid chamber (14.3) of restriction of described first piston part, and the described radial surface on the border of described the 3rd fluid chamber (14.3) of the restriction of described first piston part (16.1 ") is less than the described radial surface (16.2 ") on the border of the described second body cavity of restriction (14.2) of described the second piston portion (16.2).
6. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described first piston part (16.1) is arranged to freely to move in a first direction with respect to described the second piston portion (16.2), and this first piston part is provided with mechanical stopping piece (50), this mechanical stopping piece limits the motion of described the second piston portion (16.2) with respect to described first piston part (16.1).
According to described in claim 1 or 6 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described main body (12) is provided with the second retainer (51) cooperating with described the second piston portion (16.2), and by described the second piston portion (16.2), the movement limit in second direction arrives precalculated position to this second retainer.
8. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described fluid pressure valve device comprises the controlled fluid circulation (32) being positioned between described first-class body cavity (14.1) and described second body cavity (14.2).
9. according to claim 1 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, described fluid pressure valve device comprises the controlled fluid circulation (44) being positioned between described first-class body cavity (14.1) and described the 3rd fluid chamber (14.3).
10. according to claim 3, described in 8 and 9 for the fluid pressure valve device of operating gas crossover valve (10) controllably, it is characterized in that, the described controlled fluid circulation (32) being positioned between described first-class body cavity (14.1) and described second body cavity (14.2) comprises control valve (31), and the described controlled fluid circulation (44) being positioned between described first-class body cavity (14.1) and described the 3rd fluid chamber (14.3) comprises control valve (43), and described fluid pressure valve device utilization control valve (30 that open and/or that close, 40, 48, 31, 43) combination provides useful area as follows,
Thereby utilize predetermined fluid pressure to limit to described piston (16) applied force.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FI20125181A FI124245B (en) | 2012-02-16 | 2012-02-16 | Hydraulic valve arrangement for using a controlled gas valve in a piston combustion engine in a controlled manner |
| FI20125181 | 2012-02-16 | ||
| PCT/FI2013/050146 WO2013121100A1 (en) | 2012-02-16 | 2013-02-11 | A hydraulic valve arrangement for controllably operating a gas exchange valve of an internal combustion piston engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104169532A true CN104169532A (en) | 2014-11-26 |
| CN104169532B CN104169532B (en) | 2016-06-22 |
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ID=48014031
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380009436.0A Active CN104169532B (en) | 2012-02-16 | 2013-02-11 | For controllably operating the fluid pressure valve device of the gas exchange valve of internal combustion piston engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (2) | EP3045689A3 (en) |
| KR (1) | KR101946098B1 (en) |
| CN (1) | CN104169532B (en) |
| FI (1) | FI124245B (en) |
| WO (1) | WO2013121100A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632317A (en) * | 2015-01-30 | 2015-05-20 | 哈尔滨工程大学 | Vent valve device for high-power low-speed marine diesel engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102214301B1 (en) * | 2014-03-06 | 2021-02-08 | 바르실라 핀랜드 오이 | Gas exchange valve arrangement |
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| US3209737A (en) * | 1962-06-27 | 1965-10-05 | Mitsubishi Shipbuilding & Eng | Valve operating device for internal combustion engine |
| EP0391507A1 (en) * | 1989-04-03 | 1990-10-10 | Mitsubishi Jukogyo Kabushiki Kaisha | Valve system of internal combustion engine |
| US6223846B1 (en) * | 1998-06-15 | 2001-05-01 | Michael M. Schechter | Vehicle operating method and system |
| DE10143959A1 (en) * | 2001-09-07 | 2003-03-27 | Bosch Gmbh Robert | Hydraulically controled actuator for valve, especially gas replacement valve in combustion engine, has control piston with area of working surface(s) changing along piston displacement path |
| WO2003027449A1 (en) * | 2001-09-26 | 2003-04-03 | Robert Bosch Gmbh | Device for controlling an opening section in an internal combustion engine combustion cylinder |
| DE102008040840A1 (en) * | 2008-07-29 | 2010-02-04 | Robert Bosch Gmbh | Hydraulic controlling actuator for actuating gas shuttle valve in combustion cylinder of internal-combustion engine, has three pressure chambers, where third pressure chamber is formed by fluid chamber |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19826045A1 (en) * | 1998-06-12 | 2000-01-13 | Bosch Gmbh Robert | Method for controlling a gas exchange valve for internal combustion engines |
| DE10024268B4 (en) * | 2000-05-17 | 2012-11-29 | Robert Bosch Gmbh | Device for gasoline direct injection in a reciprocating internal combustion engine |
| DE10127205A1 (en) * | 2001-06-05 | 2002-09-05 | Bosch Gmbh Robert | Non-camshaft control of gas changing valve in an IC engine, has hydraulic working cylinder operating valve with feed line, control valve has integrated adjustable throttle for altering flow resistance to feed line |
| DE10134644A1 (en) * | 2001-07-17 | 2003-02-06 | Bosch Gmbh Robert | Electro-hydraulic valve control |
| US6899068B2 (en) | 2002-09-30 | 2005-05-31 | Caterpillar Inc | Hydraulic valve actuation system |
| DE10310300A1 (en) * | 2003-03-10 | 2004-09-23 | Robert Bosch Gmbh | Combustion engine valve actuator control method, in which the work space of the actuator is temporarily connected to a hydraulic fluid accumulator to measure a resultant pressure drop and thus the position of the actuator element |
| DE102004022447A1 (en) * | 2004-05-06 | 2005-12-01 | Robert Bosch Gmbh | Hydraulic actuator and method for operating a hydraulic actuator |
| DE102005025879A1 (en) * | 2005-06-06 | 2006-12-07 | Robert Bosch Gmbh | Hydraulic valve control`s pressure flow indicating method, for use in hydraulic system, involves calculating volume difference value from two volume values and evaluating pressure value from value based on clock pulse in real time |
| DE102007025619B4 (en) * | 2007-06-01 | 2012-11-15 | Robert Bosch Gmbh | Method and device for controlling a hydraulic actuator |
-
2012
- 2012-02-16 FI FI20125181A patent/FI124245B/en active IP Right Grant
-
2013
- 2013-02-11 EP EP15200820.7A patent/EP3045689A3/en not_active Withdrawn
- 2013-02-11 EP EP13712817.9A patent/EP2815088B1/en active Active
- 2013-02-11 WO PCT/FI2013/050146 patent/WO2013121100A1/en active Application Filing
- 2013-02-11 KR KR1020147025565A patent/KR101946098B1/en active IP Right Grant
- 2013-02-11 CN CN201380009436.0A patent/CN104169532B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3209737A (en) * | 1962-06-27 | 1965-10-05 | Mitsubishi Shipbuilding & Eng | Valve operating device for internal combustion engine |
| EP0391507A1 (en) * | 1989-04-03 | 1990-10-10 | Mitsubishi Jukogyo Kabushiki Kaisha | Valve system of internal combustion engine |
| US6223846B1 (en) * | 1998-06-15 | 2001-05-01 | Michael M. Schechter | Vehicle operating method and system |
| DE10143959A1 (en) * | 2001-09-07 | 2003-03-27 | Bosch Gmbh Robert | Hydraulically controled actuator for valve, especially gas replacement valve in combustion engine, has control piston with area of working surface(s) changing along piston displacement path |
| WO2003027449A1 (en) * | 2001-09-26 | 2003-04-03 | Robert Bosch Gmbh | Device for controlling an opening section in an internal combustion engine combustion cylinder |
| DE102008040840A1 (en) * | 2008-07-29 | 2010-02-04 | Robert Bosch Gmbh | Hydraulic controlling actuator for actuating gas shuttle valve in combustion cylinder of internal-combustion engine, has three pressure chambers, where third pressure chamber is formed by fluid chamber |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632317A (en) * | 2015-01-30 | 2015-05-20 | 哈尔滨工程大学 | Vent valve device for high-power low-speed marine diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2013121100A1 (en) | 2013-08-22 |
| EP2815088B1 (en) | 2016-02-10 |
| EP3045689A2 (en) | 2016-07-20 |
| KR101946098B1 (en) | 2019-02-08 |
| FI20125181A (en) | 2013-08-17 |
| FI124245B (en) | 2014-05-15 |
| CN104169532B (en) | 2016-06-22 |
| EP3045689A3 (en) | 2016-11-16 |
| KR20140125431A (en) | 2014-10-28 |
| EP2815088A1 (en) | 2014-12-24 |
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