CN101473111A - Engine valve device - Google Patents
Engine valve device Download PDFInfo
- Publication number
- CN101473111A CN101473111A CNA2007800230425A CN200780023042A CN101473111A CN 101473111 A CN101473111 A CN 101473111A CN A2007800230425 A CNA2007800230425 A CN A2007800230425A CN 200780023042 A CN200780023042 A CN 200780023042A CN 101473111 A CN101473111 A CN 101473111A
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- CN
- China
- Prior art keywords
- working oil
- valve device
- piston
- hydraulic actuator
- aspirating 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.)
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Classifications
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/146—Push-rods
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
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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
- F01L2305/00—Valve arrangements comprising rollers
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
An engine valve device where a valve is opened and closed in a variable manner. The device can follow high speed operation of an engine, can operate efficiently, and operates the engine valve in a variable manner. The engine valve device has an air intake valve (3) for opening and closing an intake port by pressing force of a rotating cam and a pressing force of a valve spring, a piston (23) movable in the same direction as the air intake valve (3), a cylinder section (22) for receiving the piston (23) so that it can move inside the cylinder section, a hydraulic actuator (20) having the piston (23) and the cylinder section (22), a supply/discharge pipe line (21d) communicated with a pressure chamber formed by the piston (23) and the cylinder section (22), an accumulator (50) for accumulating under pressure a hydraulic oil flowed out of the pressure chamber via the supply/discharge pipe line (21d), and a electromagnetic open/close valve (30) for controlling the flow of the hydraulic oil between the pressure chamber and the accumulator (50). The electromagnetic open/close valve (30) is placed on the supply/discharge pipe line between the hydraulic actuator (20) and the accumulator (50).
Description
Technical field
The present invention relates to engine valve device, particularly relate to the variable technology of action of engine valve device.
Background technique
Fig. 7 is the sectional side view of formation of the known engine valve device of expression, and Fig. 8 is the circuit diagram of formation of the fluid circuit of expression engine valve device shown in Figure 7.As shown in Figure 7, engine valve device 100 is constituted as the open state of keeping Aspirating valves 103 under the effect of fluidic actuator 101 via rocking arm 102.As shown in Figure 8, this engine valve device 100 have servo-actuated in the fluidic actuator 101 of rocking arm 102, stop position control valve 105 that fluid flows out from fluidic actuator 101 on the opportunity of regulation, supply with the fluid source of fluids to position control valve 105, stop fluid to flow out by position control valve 105 on the opportunity of regulation from fluidic actuator 101, fluidic actuator 101 acts on rocking arm 102, can keep the open state of Aspirating valves 103.Like this fluid source of Shi Yonging for example as shown in Figure 8, for attaching on motor and, can supplying with the compressed oil of about 210KPa～620KPa to the part of the lubrication unit 107 of motor supplying lubricating oil.On the other hand, also can pump be set independently, supply with the compressed oil (for example with reference to patent documentation 1) of 10MPa～35MPa to position control valve 105 with the lubrication unit 107 that attaches on motor.
Patent documentation 1: 2003-No. 328715 communiques of TOHKEMY.
But, as mentioned above, with attach a part at the lubrication unit on the motor 107 be fluid source and with the compressed oil of 210Kpa～620KPa when position control valve 105 is supplied with, if the rotation of motor is at a high speed, for example surpass 1000rpm, then piston 106 can not servo-actuated in the on-off action of Aspirating valves 103.Therefore, piston 106 can not arrive assigned position, can not Aspirating valves be placed open state with desirable aperture.On the other hand, with the lubrication unit 107 that attaches on motor pump is being set with being separated, when supplying with the compressed oil of 10MPa～35MPa, it is big that motor becomes, and can not avoid the significantly cost of motor to raise.In addition, fluidic actuator 101 acts at every turn, all supplies with and discharges from the lubrication unit 107 that attaches on motor, and therefore, energy loss is very big.
Summary of the invention
The present invention In view of the foregoing develops, its purpose is, a kind of engine valve device is provided, though will attach the part of the lubrication unit on motor apply flexibly as hydraulic power make the action variable, also can servo-actuated in the high speed rotating of motor, and can turn round efficiently.
For solving above-mentioned problem and realizing purpose, the invention provides a kind of engine valve device, it possesses: the cam that connects rotation with bent axle; Rocking arm with the action of cam interlock; Rocking arm and spring action and open and close the Aspirating valves of intakeport, described engine valve device is characterised in that to have: the piston that can move on the direction identical with described Aspirating valves; Accommodate described piston and make the clutch release slave cylinder of described piston portion motion within it; The hydraulic actuator that constitutes by described piston and described clutch release slave cylinder; The hydraulic pipe line that is communicated with the pressure chamber that constitutes by described piston and described clutch release slave cylinder; Via the energy storage apparatus of described hydraulic pipe line to carrying out accumulation of energy from the working oil of described pressure chamber outflow; The electromagnetic opening and closing valve that the circulation of the working oil between described pressure chamber and the described energy storage apparatus is controlled, wherein, constitute oil hydraulic circuit by described hydraulic actuator, described hydraulic pipe line, described energy storage apparatus and described electromagnetic opening and closing valve, described electromagnetic opening and closing valve is disposed on the hydraulic pipe line between described hydraulic actuator and the described energy storage apparatus.
In addition, the invention provides a kind of engine valve device, it possesses: the cam that connects rotation with bent axle; Rocking arm with the action of cam interlock; Rocking arm and spring action and open and close the Aspirating valves of intakeport, described engine valve device is characterised in that, has hydraulic actuator, energy storage apparatus and electromagnetic opening and closing valve and constitute oil hydraulic circuit, described hydraulic actuator moves forward into the action work by the switching of Aspirating valves, and under the situation of working oil being enclosed the pressure chamber, stop the obturation of the Aspirating valves of the state that is in out to move, described energy storage apparatus carries out inaccessiblely the working oil that flows out from the pressure chamber of hydraulic actuator being carried out accumulation of energy when mobile at Aspirating valves, open at Aspirating valves that the pressure chamber to hydraulic actuator supplies with working oil when mobile, described electromagnetic opening and closing valve is controlled to the outflow of energy storage apparatus from hydraulic actuator working oil, and described electromagnetic opening and closing valve is arranged between described hydraulic actuator and the described energy storage apparatus.
In addition, the present invention provides engine valve device on the basis of foregoing invention, it is characterized in that, possesses working oil supplier from working oil to described oil hydraulic circuit that supply with.
In addition, the present invention provides engine valve device on the basis of foregoing invention, it is characterized in that, described working oil supplier is to attach on motor and to the lubrication unit of motor supplying lubricating oil.
In addition, the present invention is on the basis of foregoing invention, engine valve device is provided, it is characterized in that, also be provided with the auxiliary piping of allowing that working oil flows out to energy storage apparatus from the pressure chamber of hydraulic actuator, described auxiliary piping has the mouth that is in regulation opening when interval in servo-actuated in the piston position to the hydraulic actuator that closes the Aspirating valves that direction moves.
In addition, the present invention is on the basis of foregoing invention, engine valve device is provided, it is characterized in that, be provided with one-way valve between working oil supplier and described oil hydraulic circuit, this one-way valve just hour is supplied with working oil from the working oil supplier to oil hydraulic circuit at the hydraulic pressure of described oil hydraulic circuit than the hydraulic pressure of working oil supplier.
In addition, the present invention provides engine valve device on the basis of foregoing invention, it is characterized in that, the impact the when pressure chamber of described hydraulic actuator constitutes the Aspirating valves obturation cushions.
In addition, the present invention provides engine valve device on the basis of foregoing invention, it is characterized in that, possesses: between cam and rocking arm and from the push rod of cam to rocking arm transmission action; With the force application device of rocking arm to the direction application of force of connecting airtight with push rod.
Engine valve device of the present invention possesses: energy storage apparatus, and it carries out inaccessible when mobile at Aspirating valves, the working oil that flows out from the pressure chamber of hydraulic actuator is carried out accumulation of energy, opens when mobile at Aspirating valves, supplies with working oil to the pressure chamber of hydraulic actuator; The electromagnetic opening and closing valve that working oil is controlled to the outflow of energy storage apparatus from hydraulic actuator, constitute oil hydraulic circuit by this energy storage apparatus and electromagnetic opening and closing valve, and between hydraulic actuator and energy storage apparatus, be provided with electromagnetic opening and closing valve, therefore, because Aspirating valves is made as open state accurately, so but servo-actuated in the high speed rotating of motor and can turn round efficiently.
In addition, in engine valve device of the present invention, owing to attach on motor and and supply with working oil to oil hydraulic circuit to the lubrication unit of motor supplying lubricating oil, therefore, the lubrication unit that does not need and attach on motor is provided with oil pump independently, do not need motor is maximized yet, rise if like this then can suppress the cost of motor.
Description of drawings
Fig. 1 is the concept map of the engine valve device of expression embodiment of the present invention;
Fig. 2-the 1st represents the schematic representation of the effect of engine valve device shown in Figure 1, is the figure of the blocked state of expression Aspirating valves;
Fig. 2-the 2nd represents the schematic representation of the effect of engine valve device shown in Figure 1, is the figure of the full-gear of expression Aspirating valves;
Fig. 2-the 3rd represents the schematic representation of the effect of engine valve device shown in Figure 1, is the figure of the inaccessible initial state of expression Aspirating valves;
Fig. 2-the 4th represents the schematic representation of the effect of engine valve device shown in Figure 1, is the figure that the expression Aspirating valves is closed to the state of regulation aperture;
Fig. 2-the 5th represents the schematic representation of the effect of engine valve device shown in Figure 1, is the figure of the full-shut position of expression Aspirating valves;
Fig. 3 is the hydraulic circuit diagram of engine valve device shown in Figure 1;
Fig. 4 is the figure of the relation of the suction stroke cam angle of rotation of expression engine valve device shown in Figure 1 and valve-lift amount;
Fig. 5 is the flow chart of the control of explanation engine valve device shown in Figure 1;
Fig. 6 is the time diagram on control opportunity of explanation engine valve device shown in Figure 1;
Fig. 7 is the sectional side view of the formation of the known engine valve device of expression;
Fig. 8 is the circuit diagram of formation of the fluid circuit of expression engine valve device shown in Figure 7.
Symbol description
1 engine valve device
2 intakepories
3 Aspirating valvess
3a valve portion
The 3b bar
4 valve springs
5 crossheads
9 rocking arms
The 9a press part
The 9b operating member
The 9c groove
13 push rods
14 tappet arms
15 Returnning springs
18 cams
20 hydraulic actuators
21 working cylinders
The 21a recess
21b first pipeline
21c second pipeline
21d is for the comb road
21e flows out pipeline
22 clutch release slave cylinder portions
22a path chamber
Chamber, the big footpath of 22b
The 22b1 oil groove
23 pistons
The 23a piston portion
The 23b buffer part
The 23b1 pod
The 23c link rod part
24 gap sensors
30 electromagnetic opening and closing valves
40 control unit of engine (ECU)
50 accumulators
52 accumulation of energy portions
55 clutch release slave cylinders
56 plungers
57 pressure springs
60 oil hydraulic circuits
61 attach the lubrication unit on motor
62 one-way valves
63 safety valves
64 food trays
The CH working-cylinder head
Embodiment
Below, the engine valve device of present invention will be described in detail with reference to the accompanying mode of execution.In addition, the present invention is not limited by this mode of execution.
Fig. 1 is the concept map of the engine valve device of expression embodiment of the present invention, Fig. 2 is the schematic representation of the effect of expression engine valve device shown in Figure 1, Fig. 3 is the hydraulic circuit diagram of engine valve device shown in Figure 1, Fig. 4 is the figure of the relation of cam angle of rotation in the suction stroke of expression engine valve device shown in Figure 1 and valve-lift amount, Fig. 5 is the flow chart of the control of explanation engine valve device shown in Figure 1, and Fig. 6 is the time diagram on control opportunity of explanation engine valve device shown in Figure 1.
The engine valve device 1 of embodiment of the present invention is applied to the engine valve device of 4 stroke diesel engine.
Diesel engine has working cylinder and working-cylinder head CH.Be provided with the clutch release slave cylinder that makes the tubular that engine piston EP can slide on above-below direction on the working cylinder.
On working-cylinder head, be provided with to logical a pair of intakeport 2 of clutch release slave cylinder extrapolation and not shown a pair of relief opening.Be provided with Aspirating valves 3 in each intakeport 2, Aspirating valves 3 moves along Fig. 1 above-below direction, and inaccessible or open intakeport 2 is provided with not shown outlet valve in each relief opening, and outlet valve moves along the vertical direction, obturation or open row gas port.
On the bar 3b of the Aspirating valves 3 of inserting logical intakeport 2 valve spring 4 is installed, it is with the 3a of valve portion of the Aspirating valves 3 direction application of force to inaccessible intakeport 2.Equally, on the bar of the outlet valve of inserting logical relief opening not shown valve spring is installed, it is with the valve portion of the outlet valve direction application of force to inaccessible relief opening.
The crosshead 5 that is the T font is seen in the side that possesses the boom end of pushing a pair of Aspirating valves 3 simultaneously above working-cylinder head CH.Axle 6 guiding that crosshead 5 is be arranged in parallel by the moving direction with Aspirating valves 3 and outlet valve can above-below direction lifting in Fig. 1.Therefore, when crosshead 5 was descended, crosshead 5 was pushed the boom end of a pair of Aspirating valves 3, the application of force of antagonism valve spring 4 and Aspirating valves 3 is open.
Possesses the adjusting screw 7 that the mode of connecting airtight according to Aspirating valves 3 and crosshead 5 is regulated at a wrist 5a of crosshead 5 (wrist in left side among Fig. 1).Adjusting screw 7 can be screwed into respect to crosshead 5, the gap of the Aspirating valves 3 in can regulate and a pair of Aspirating valves 3 (Aspirating valves in left side among Fig. 1).For example, when can intakeport 2 be opened according to another Aspirating valves 3, an Aspirating valves 3 is regulated intakeport 2 open modes.On this adjusting screw 7, twist and closed locking nut 8, locking nut 8 and crosshead 5 are connected airtight, can prevent that thus adjusting screw 7 is loosening.
Be provided with rocking arm 9 above in Fig. 1 of crosshead 5.Rocking arm 9 can serve as that axle rotates with pitman arm shaft 10, and an end (left part among Fig. 1) becomes the press part 9a that pushes crosshead 5, and the other end (right part among Fig. 1) becomes operating member 9b.The press part 9a of rocking arm 9 can push the substantial middle portion of crosshead 5.Therefore, when rocking arm 9 counterclockwise rotated in Fig. 1, the press part 9a of rocking arm 9 pushed crosshead 5, Aspirating valves 3 open intakepories 2.On the other hand, when rocking arm 9 clockwise direction in Fig. 1 rotates, by the application of force of valve spring 4, Aspirating valves 3 inaccessible intakepories 2, and crosshead 5 is risen.Be formed with to overlook in the central authorities of press part 9a and see the groove 9c that is the U word shape.
Operating member 9b at rocking arm 9 twists the adjusting screw rod 11 that closes the gap of regulating press part 9a and crosshead 5.Adjusting screw rod 11 1 ends have semi-spherical shape, are formed with external screw thread in the other end.Closed locking nut 12 twisting to close on the adjusting screw rod 11 of the other end of rocking arm 9, to twist, connected airtight, can prevent that adjusting screw rod 11 is loosening by making locking nut 12 and rocking arm 9.
An end that is semi-spherical shape of adjusting screw rod 11 is contained in an end of push rod 13.Be formed with the recess 13a of semi-spherical shape in an end of push rod 13, it can accommodate the end with semi-spherical shape of adjusting screw rod 11.
Push rod 13 rotates rocking arm 9 to counter clockwise direction in Fig. 1, as shown in Figure 2, the other end 13b of push rod 13 is contained in the push rod accommodation section 14a that is provided with above the wrist of tappet arm 14.
As shown in Figure 1, between the operating member 9b of rocking arm 9 and working-cylinder head CH, set up Returnning spring 15.Returnning spring 15 can be kept the state that an end of adjusting screw rod 11 is contained in the recess 13a of push rod 13 with rocking arm 9 clockwise direction application of force in Fig. 1.In addition, Returnning spring 15 also can be the helical spring of being turned round around pitman arm shaft 10 packages so long as the parts of rocking arm 9 clockwise direction application of force in Fig. 1 are got final product.Under this situation, a helical spring end is fixed on the rocking arm 9, the other end is fixed on the working-cylinder head CH.
As shown in Figure 2, to be installed to be to serve as that axle rotates with tappet axle 16 to tappet arm 14.Therefore, when tappet arm 14 clockwise direction in Fig. 2 rotates, press push rod 13 on the tappet arm 14 and rocking arm 9 is counterclockwise rotated in Fig. 2.
Rotation is equipped with roller follower 17 freely below the wrist of tappet arm 14.Below roller follower 17, rotatably be provided with the cam 18 that rolls and contact with this roller follower 17.Cam 18 connects with the not shown bent axle of motor and rotates, and makes Aspirating valves 3 move (rising) via tappet arm 14, push rod 13, rocking arm 9 and crosshead 5, can open intakeport 2.Thereby, control the open opportunity of intakeport 2 and the valve-lift amount of Aspirating valves 3 by the outer shape (cam profile) of cam 18.Valve-lift amount is to be 0 when closing and to move this situation as lifting to the direction of opening, and gets positive value this moment.
A bent axle and an end are linked to the connecting rod of the engine piston EP that slides in clutch release slave cylinder the other end links.Thereby, can in suction stroke, open and close Aspirating valves 3, inaccessible Aspirating valves 3 in compression stroke, outburst stroke, exhaust stroke.
As shown in Figure 1, above crosshead 5, be provided with hydraulic actuator 20.Hydraulic actuator 20 is according to the front end of the link rod part 23c of piston 23 and crosshead 5 butts and can set with the action linkage manner of crosshead 5, push crosshead 5 on the opportunity of regulation, no matter the action of above-mentioned cam 18, tappet arm 14, push rod 13 and rocking arm 9 how, can both keep the open state of Aspirating valves 3.
The hydraulic actuator 20 that is applied to present embodiment is formed with clutch release slave cylinder portion 22 for single-lift on working cylinder 21, can accommodate electromagnetic opening and closing valve 30 is installed.
On working cylinder 21, be formed with the confession comb road 21d that is communicated with the delivery outlet 30b of electromagnetic opening and closing valve 30.In addition, also be formed with the first pipeline 21b that is communicated with the delivery outlet 50a of accumulator 50 described later.The first pipeline 21b is communicated with the inlet opening 30a and the outflow pipeline 21e described later of electromagnetic opening and closing valve 30 by the second pipeline 21c.
Clutch release slave cylinder portion 22 is formed by columnar path chamber 22a that constitutes the pressure chamber and big footpath chamber 22b.The end of big footpath chamber 22b is open according to piston 23 insertable modes, and by piston 23 obturations.Be formed with path chamber 22a at the big directly the other end of chamber 22b, this path chamber 22a and connection consistent with the axle of big footpath chamber 22b.Path chamber 22a is communicated with supplying comb road 21d.Boundary portion at big footpath chamber 22b and path chamber 22a is formed with step 22c.
Be formed with oil groove 22b1 in the big directly part of the regulation of chamber 22b.On oil groove 22b1, be formed with the outflow pipeline 21e that is communicated with the second pipeline 21c.
Contain the piston 23 that slides along the axle direction (above-below direction among Fig. 1) of these big footpaths chamber 22b and path chamber 22a in clutch release slave cylinder portion 22.Piston 23 has piston portion 23a, buffer part 23b and link rod part 23c.Piston portion 23a is the part of sliding at the big footpath of clutch release slave cylinder portion 22 chamber 22b.Buffer part 23b is the part that is contained in the path chamber 22a of clutch release slave cylinder portion 22, and is located at axle direction one end (top of piston portion among Fig. 1) of piston portion 23a.Buffer part 23b can cushion Aspirating valves 3 impact when inaccessible by the interaction with the path chamber 22a of clutch release slave cylinder portion 22, and under this meaning, the mode of pressure chamber's impact when inaccessible with buffering Aspirating valves 3 constitutes.
Particularly, buffer part 23b has the buffering shape of the impact of a buffering Aspirating valves 3 when inaccessible (Aspirating valves 3 fall time).The buffering shape for example is a plurality of pod 23b1 (pod of present embodiment is 4) that form towards front end from the periphery root of buffer part 23b, when buffer part 23b is contained in path chamber 22a, the working oil that is stranded in the bight, upper end of big footpath chamber 22b flows out by pod 23b1, the impact in the time of can alleviating buffer part 23b thus and be contained in path chamber 22a.Consequently, the impact when Aspirating valves that available buffer connects with the piston 23 of hydraulic actuator 20 3 is inaccessible prevents the caused destruction of impact when the 3a of valve portion by Aspirating valves 3 falls.
In addition, the buffering shape is not limited to pod 23b1, for example also can form buffer part 23b to subtract thin cone-shaped from root gradually towards front end.In addition, also can with from the bottom towards big footpath chamber 22b gradually the cone-shaped of overstriking form path chamber 22a.The part of link rod part 23c for stretching out to the outside from clutch release slave cylinder portion 22 is located at the end different with buffer part 23b (being the below of piston portion 23a among Fig. 1) on the axle direction of piston portion 23.Link rod part 23c has subtracting the cone-shaped that thin mode forms from root gradually towards front end, and inserts the groove 9c on the logical press part 9a that is formed at rocking arm 9, can not produce with rocking arm 9 and not push crosshead 5 intrusively.Thereby link rod part 23c can push crosshead 5 respectively independently with rocking arm 9.
Side at the link rod part 23c of piston 23 is provided with gap sensor (measuring backlash device) 24.Gap sensor 24 is measured the gap between link rod parts 23 and the gap sensor 24, and is connected with control unit of engine (ECU) 40.Gap sensor 24 for example can be measured gap between itself and the link rod part 23c by measuring foucault current.Control unit of engine 40 can monitor the action of hydraulic actuator 20 by monitoring gap between that be measured to and the link rod part 23c of gap sensor 24.Particularly, when clutch release slave cylinder portion 22 stretched out, the gap reduced at link rod part 23c, and when clutch release slave cylinder portion 22 shrank back, the gap increased at link rod part 23c, therefore, can monitor the action of hydraulic actuator 20 by monitoring the gap.
Recess 21a at working cylinder 21 contains electromagnetic opening and closing valve 30.Electromagnetic opening and closing valve 30 is the twoport electromagnetic opening and closing valves with inlet opening 30a and delivery outlet 30b.Inlet opening 30a is communicated with the second pipeline 21c of working cylinder 21, and delivery outlet 30b is communicated with for comb road 21d with working cylinder 21.Electromagnetic opening and closing valve 30 except that having guiding valve 31, also has not shown spring and solenoid in inside.This electromagnetic opening and closing valve 30 is that spring is pushed guiding valve 31 and inlet opening 30a and delivery outlet 30b are communicated with in the normal state, when to the solenoid excitation, and the application of force of guiding valve 31 antagonism springs and the connected state that cuts off inlet opening 30a and delivery outlet 30b.Therefore, electromagnetic opening and closing valve 30 is changeable is that working oil is for row's state and working oil dissengaged positions.
Therefore, when via the first pipeline 21b that is formed at working cylinder 21 and the second pipeline 21c, electromagnetic opening and closing valve 30 and with working oil when being formed at the supplying with of working cylinder 21 for comb road 21d, working oil is fed into big footpath chamber 22b via path chamber 22a.So working oil is released (Fig. 1 be decline) with piston 23 from clutch release slave cylinder portion 22 to the piston portion 23a effect of piston 23, link rod part 23c stretches out below in Fig. 1.Afterwards, when the solenoid to electromagnetic opening and closing valve 30 carries out excitation, cut off the connected state of inlet opening 30a and delivery outlet 30b.Under this state, when link rod part 23c is pressed on clutch release slave cylinder portion 22 sides (top among Fig. 1), piston 23 is pressed into clutch release slave cylinder portion 22 up to the inaccessible oil groove 22b1 that is communicated with the outflow pipeline 21e of working cylinder 21 of the piston portion 23a of piston 23, and working oil is enclosed path chamber 22a and big footpath chamber 22b.At this moment, piston 23 is stoped by the working oil among inclosure path chamber 22a and the big footpath chamber 22b and stops.
Afterwards, if the solenoid of electromagnetic opening and closing valve 30 is taken off magnetic, then inlet opening 30a and delivery outlet 30b become connected state once more.When under this state the link rod part 23c of piston 23 being gone up when pressing to clutch release slave cylinder portion 22 sides (top among Fig. 1), piston 23 rises, and working oil flows out for comb road 21d from working cylinder 21.The working oil that flows out flows out to the outside of hydraulic actuator 20 gradually via the delivery outlet 30b of electromagnetic opening and closing valve 30 and inlet opening 30a, the second pipeline 21c and the first pipeline 21b.Afterwards, the path chamber 22a with the buffer part 23b of piston 23 is contained in clutch release slave cylinder portion 22 finishes a series of effect of hydraulic actuator 20.
On electromagnetic opening and closing valve 30, be connected with control unit of engine 40.Excitation opportunity, the excitation time of control unit of engine 40 control electromagnetic opening and closing valves 30, it can control electromagnetic opening and closing valve 30 arbitrarily with millisecond (1/1000 second) unit.
The delivery outlet 50a that on the first pipeline 21b of working cylinder 21, connects accumulator 50.Accumulator 50 becomes the energy storage apparatus that hydraulic pressure is carried out accumulation of energy, and the accumulator 50 of present embodiment is the mechanical type accumulator.
As shown in Figure 1, accumulator has above-mentioned delivery outlet 50a, the output pipe 50b that extends of this delivery outlet 50a, the intake line 50c, the inlet opening 50d that is communicated with intake line 50c that report to the leadship after accomplishing a task with this output pipe 50b certainly.Intake line 50c is communicated with accumulation of energy portion 52.
Accumulation of energy portion 52 has the clutch release slave cylinder 55 that is formed on the accumulator main body.Clutch release slave cylinder 55 is communicated with intake line 50c, the working oil that can flow into the working oil supplied with from inlet opening 50d, supply with from delivery outlet 50a.Have the plunger 56 that slides along the axle direction of clutch release slave cylinder 55 in the inside of clutch release slave cylinder 55, with the pressure spring 57 of plunger 56 to the diapire of clutch release slave cylinder 55 (among the figure towards the left) application of force.
Thereby although supply with working oil from the inlet opening 50d of accumulator 50, working oil is pushed plunger 56 to side (right side side among Fig. 1), and plunger 56 can not resist the application of force of pressure spring 57, thereby working oil flows out from delivery outlet 50a.On the other hand, when flow out from hydraulic actuator 20 and than the working oil of the working oil high pressure of supplying with from inlet opening 50d when the delivery outlet 50a of accumulator 50 supplies with, working oil is pushed plunger 56 to side (right side side among Fig. 1), plunger 56 resists the application of force of pressure springs 57 and moves to side (right side side among the figure).At this moment, store (accumulation of energy) working oil in accumulation of energy portion 52.
As shown in Figure 3, these hydraulic actuators 20, electromagnetic opening and closing valve 30, accumulator 50 constitute oil hydraulic circuit 60.This oil hydraulic circuit 60 attaches on motor, and can be from supply with the working oil of low pressure to the lubrication unit 61 of motor supplying lubricating oil.Be equipped with one-way valve 62 attaching between lubrication unit on the motor 61 and oil hydraulic circuit 60.One-way valve 62 is just supplied with working oil from the lubrication unit 61 that attaches on motor to oil hydraulic circuit 60 than the hydraulic pressure hour ability of attaching at the lubrication unit on the motor 61 at the hydraulic pressure of oil hydraulic circuit 60, and working oil can be from oil hydraulic circuit 60 effluents to the lubrication unit 61 that attaches on motor.
In addition, between one-way valve 62 and above-mentioned oil hydraulic circuit 60, be provided with safety valve 63.When safety valve 63 exceeds predefined pressure at the hydraulic pressure of oil hydraulic circuit 60, the working oil of oil hydraulic circuit 60 can be discharged to the food tray 64 of motor.
As mentioned above, the control unit of engine 40 that is connected with gap sensor 24 and electromagnetic opening and closing valve 30 as shown in Figure 6, the engine piston EP that detects which clutch release slave cylinder based on the clutch release slave cylinder judgment signal (G signal) of illustrated TDC (Top Dead Center) sensor (clutch release slave cylinder judgment signal output unit) input never is positioned at top dead center.In addition, control unit of engine 40 calculates rotating speed based on the rotary speed detecting signal (Ne signal) of illustrated crank angle sensor (rotary speed detecting signal output unit) input never, and begins the umber of pulse of rotary speed detecting signal (rectangular wave) is counted when the engine piston EP that makes the clutch release slave cylinder (for example clutch release slave cylinder Fig. 6 " 5 ") that postpones inaccessible opportunity is positioned at top dead center.When the umber of pulse of the rotary speed detecting signal that is counted arrived pre-set VVA startup setting pulse, control unit of engine 40 was connected the VVA actuating signals, and with predefined VVA retention time Tw electromagnetic opening and closing valve 30 is carried out excitation.
According to the engine valve device 1 that possesses above-mentioned oil hydraulic circuit 60,, supply with working oil to oil hydraulic circuit 60 from the lubrication unit 61 that attaches on motor by making engine start.Particularly, press the sequentially feeding working oil of accumulator 50, electromagnetic opening and closing valve 30, hydraulic actuator 20 via one-way valve 62.Therefore, working oil is filled in electromagnetic opening and closing valve 30, the hydraulic actuator 20.
Then, if motor action, then connect with the bent axle of motor, sequence delivery power according to cam 18, tappet arm 14, push rod 13, rocking arm 9, crosshead 5, in the suction stroke of motor, open and close intakepories 2 by Aspirating valves 3, in the compression stroke of motor and outburst stroke, exhaust stroke, by Aspirating valves 3 inaccessible intakepories 2.
In the compression stroke of motor and outburst stroke, exhaust stroke, shown in Fig. 2-1, Aspirating valves 3 is inaccessible Aspirating valves 2 by the application of force of valve spring 4.Relation shown in the angle of rotation of the cam 18 of this moment and the occlusion areas that valve-lift amount has Fig. 4.That is it is irrelevant and be 0 relation, to have an angle of rotation of valve-lift amount and cam 18.
When motor began suction stroke, from the sequence delivery power of cam 18 according to tappet arm 14, push rod 13, rocking arm 9, crosshead 5, Aspirating valves 3 promoted, and thus, intakeport 2 is open gradually.Relation shown in the opening acting zone that the cam angle of rotation of this moment and valve-lift amount have Fig. 4.That is, has the increase of the angle of rotation that valve-lift amount follows cam 18 and the relation that increases gradually.
At this moment, the link rod part 23c of piston 23 be by will being stored in path chamber 22a and the big footpath chamber 22b that working oil in the accumulator 50 is supplied in clutch release slave cylinder portion 22 gradually, with crosshead 5 butts on one side gradually stretch out (in Fig. 1 below) on one side.Particularly, according to the sequentially feeding working oil of electromagnetic opening and closing valve 30, hydraulic actuator 20.At this, in accumulator 50, do not store under the work oil condition, gradually supply with working oil via one-way valve 62 to oil hydraulic circuit 60 from the lubrication unit 61 that attaches on motor.
And when valve-lift amount reached maximum, shown in Fig. 2-2, intakeport 2 became full-gear.
Afterwards, shown in Fig. 2-3, by the application of force of valve spring 4 and Returnning spring 15, crosshead 5, rocking arm 9, push rod 13, tappet arm 14 servo-actuateds are in cam 18, and Aspirating valves 3 is inaccessible gradually with intakeport 2.Relation shown in the blocking action zone that the cam angle of rotation of this moment and valve-lift amount have Fig. 4.That is, has the increase of the angle of rotation that valve-lift amount follows cam 18 and the relation that reduces gradually.
At this moment, piston 23 is contained in clutch release slave cylinder portion 22 gradually, and the working oil of the path chamber 22a of clutch release slave cylinder portion 22 and big footpath chamber 22b is stored in the accumulator 50.Thereby hydraulic actuator 20 has the function of reciprocating pump.Particularly, working oil is via electromagnetic opening and closing valve 30, hydraulic actuator 20 and be stored in the accumulator 50.
And as shown in Figure 4, when valve-lift amount reaches minimum promptly 0 the time, shown in Fig. 2-5, Aspirating valves 3 becomes full-shut position.
On the other hand, in blocking action zone shown in Figure 4, when electromagnetic opening and closing valve 30 is carried out excitation, the application of force of guiding valve 31 antagonism springs and the connected state that cuts off inlet opening 30a and delivery outlet 30b.That is, electromagnetic opening and closing valve 30 supplies row's state transitions to the working oil dissengaged positions from working oil.So piston 23 is pressed into the oil groove 22b1 that is communicated with the outflow pipeline 21e of working cylinder 21 until the piston portion 23a of piston 23 obturation in the clutch release slave cylinder portion 22, afterwards, in the path chamber of clutch release slave cylinder portion 22 22a and big footpath chamber 22b, enclose working oil.Thereby piston 23 is stoped by the working oil of inclosure path chamber 22a and big footpath chamber 22b and stops.
So the link rod part 23c of piston 23 pushes crosshead 5, shown in Fig. 2-4, Aspirating valves 3 is kept opened state with the aperture of regulation.That is, in suction stroke, postpone the inaccessible opportunity of the intakeport 2 that Aspirating valves 3 carries out.Because be to set oil groove 22b1 in the inside of clutch release slave cylinder portion 22, and the mechanism of the inaccessible oil groove 22b1 of piston portion 23a, so can keep open state with identical aperture.The cam angle of rotation of this moment and valve-lift amount have the relation shown in the inaccessible delay zone among Fig. 4.That is, also be certain relation even have the angle of rotation increase valve-lift amount of cam 18.
Like this, even push crosshead 5 at the link rod part 23c of piston 23, and under the aperture situation about keeping of Aspirating valves 3 with regulation, rocking arm 9 also can connect airtight with push rod 13 under the application of force effect of Returnning spring 15, and is controlled by the external diameter shape (cam profile) of cam 18.Thereby push rod 13 can not come off from rocking arm 9, can produce the gap between crosshead 5 and rocking arm 9.
When electromagnetic opening and closing valve 30 being taken off magnetic after the stipulated time, inlet opening 30a and delivery outlet 30b become connected state once more.Therefore, under the application of force effect of valve spring 4, Aspirating valves 3 is inaccessible gradually with intakeport 2.
At this moment, crosshead 5 is pushed piston 23, and piston 23 is contained in the clutch release slave cylinder portion 22 once more gradually, and the working oil of the path chamber 22a of clutch release slave cylinder portion 22 and big footpath chamber 22b is stored in the accumulator 50.
And as shown in Figure 4, when valve-lift amount is minimum promptly 0 the time, shown in Fig. 2-5, by Aspirating valves 3, intakeport 2 becomes full-shut position.
Like this, inaccessible delay on opportunity owing to the intakeport 2 that Aspirating valves 3 is carried out, so control unit of engine 40 is as Fig. 5 and shown in Figure 6, when the engine piston EP that makes the clutch release slave cylinder (for example clutch release slave cylinder among Fig. 6 " 5 ") that postpones inaccessible opportunity is positioned at top dead center (step S1: "Yes"), the counting (step S2) of the umber of pulse of beginning rotary speed detecting signal.Then, arrive predefined VVA in the umber of pulse of rotary speed detecting signal and started (step S3: "Yes"), connect VVA actuating signal (step S4) when setting pulse.Like this, when the VVA actuating signal is connected, electromagnetic opening and closing valve 30 is carried out excitation (step S5) with predefined VVA retention time Tw.Afterwards, by repeating such circulation, control according to the mode that postpones on inaccessible opportunity of the intakeport 2 that Aspirating valves 3 is carried out.
Utilizability on the industry
As mentioned above, the engine valve device of the present invention engine valve variable to the action of engine valve Device is useful, is particularly useful for the engine valve of Diesel engine.
Claims (8)
1, a kind of engine valve device, it possesses:
The cam that connects rotation with bent axle;
Rocking arm with the action of cam interlock;
Rocking arm and spring action and open and close the Aspirating valves of intakeport,
Described engine valve device is characterised in that to have:
The piston that can on the direction identical, move with described Aspirating valves;
Accommodate described piston and make the clutch release slave cylinder of described piston portion motion within it;
The hydraulic actuator that constitutes by described piston and described clutch release slave cylinder;
The hydraulic pipe line that is communicated with the pressure chamber that constitutes by described piston and described clutch release slave cylinder;
Via the energy storage apparatus of described hydraulic pipe line to carrying out accumulation of energy from the working oil of described pressure chamber outflow;
The electromagnetic opening and closing valve that the circulation of the working oil between described pressure chamber and the described energy storage apparatus is controlled,
Wherein, constitute oil hydraulic circuit by described hydraulic actuator, described hydraulic pipe line, described energy storage apparatus and described electromagnetic opening and closing valve,
Described electromagnetic opening and closing valve is disposed on the hydraulic pipe line between described hydraulic actuator and the described energy storage apparatus.
2, a kind of engine valve device, it possesses:
The cam that connects rotation with bent axle;
Rocking arm with the action of cam interlock;
Rocking arm and spring action and open and close the Aspirating valves of intakeport,
Described engine valve device is characterised in that,
Have hydraulic actuator, energy storage apparatus and electromagnetic opening and closing valve and constitute oil hydraulic circuit,
Described hydraulic actuator moves forward into the action work by the switching of Aspirating valves, and stops the obturation of the Aspirating valves of the state that is in out to move under the situation of working oil being enclosed the pressure chamber,
Described energy storage apparatus carries out inaccessiblely the working oil that flows out from the pressure chamber of hydraulic actuator being carried out accumulation of energy when mobile at Aspirating valves, and open when mobile at Aspirating valves and supply with working oil to the pressure chamber of hydraulic actuator,
Described electromagnetic opening and closing valve is controlled to the outflow of energy storage apparatus from hydraulic actuator working oil,
Described electromagnetic opening and closing valve is arranged between described hydraulic actuator and the described energy storage apparatus.
3, engine valve device as claimed in claim 1 or 2 is characterized in that,
Possesses working oil supplier from working oil to described oil hydraulic circuit that supply with.
4, engine valve device as claimed in claim 3 is characterized in that,
Described working oil supplier is to attach on motor and to the lubrication unit of motor supplying lubricating oil.
5, as each described engine valve device in the claim 1～4, it is characterized in that,
Also be provided with the auxiliary piping of allowing that working oil flows out to energy storage apparatus from the pressure chamber of hydraulic actuator,
Described auxiliary piping has the mouth that is in regulation opening when interval in servo-actuated in the piston position to the hydraulic actuator that closes the Aspirating valves that direction moves.
6, as each described engine valve device in the claim 3～5, it is characterized in that,
Be provided with one-way valve between working oil supplier and described oil hydraulic circuit, this one-way valve just hour is supplied with working oil from the working oil supplier to oil hydraulic circuit at the hydraulic pressure of described oil hydraulic circuit than the hydraulic pressure of working oil supplier.
7, as each described engine valve device in the claim 1～6, it is characterized in that,
Impact when the pressure chamber of described hydraulic actuator constitutes the Aspirating valves obturation cushions.
8, as each described engine valve device in the claim 2～7, it is characterized in that,
Possess:
Between cam and rocking arm and from the push rod of cam to rocking arm transmission action;
With the force application device of rocking arm to the direction application of force of connecting airtight with push rod.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP182121/2006 | 2006-06-30 | ||
| JP2006182121 | 2006-06-30 | ||
| PCT/JP2007/062630 WO2008001699A1 (en) | 2006-06-30 | 2007-06-22 | Engine valve device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101473111A true CN101473111A (en) | 2009-07-01 |
| CN101473111B CN101473111B (en) | 2011-08-31 |
Family
ID=38845464
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800230425A Expired - Fee Related CN101473111B (en) | 2006-06-30 | 2007-06-22 | Engine valve device |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20090199796A1 (en) |
| EP (1) | EP2039892B1 (en) |
| JP (1) | JPWO2008001699A1 (en) |
| KR (1) | KR101083613B1 (en) |
| CN (1) | CN101473111B (en) |
| WO (1) | WO2008001699A1 (en) |
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| CN105804827A (en) * | 2016-05-04 | 2016-07-27 | 哈尔滨工程大学 | Piezoelectrically-controlled pressure-intensified valve system |
| CN106870178A (en) * | 2015-12-14 | 2017-06-20 | 现代自动车株式会社 | Gradual braking device and its control method |
| CN110185513A (en) * | 2019-07-01 | 2019-08-30 | 贵州大学 | A kind of electric-liquid type variable valve timing regulating device |
| CN111535894A (en) * | 2020-04-28 | 2020-08-14 | 一汽解放汽车有限公司 | Electric control hydraulic type air valve system and engine |
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| JP2010121571A (en) * | 2008-11-20 | 2010-06-03 | Komatsu Ltd | Variable valve device and control method thereof |
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| DE102011005472A1 (en) * | 2011-03-14 | 2012-09-20 | Schaeffler Technologies Gmbh & Co. Kg | Accumulator unit for a camshaft and reciprocating piston for an accumulator unit |
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| KR101382327B1 (en) * | 2012-10-17 | 2014-04-08 | 현대자동차 주식회사 | Variable valve lift device |
| FI20135003L (en) * | 2013-01-03 | 2014-07-04 | Waertsilae Finland Oy | Drain valve device and method for checking closure of a drain valve |
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- 2007-06-22 US US12/308,716 patent/US20090199796A1/en not_active Abandoned
- 2007-06-22 CN CN2007800230425A patent/CN101473111B/en not_active Expired - Fee Related
- 2007-06-22 KR KR1020087030930A patent/KR101083613B1/en not_active IP Right Cessation
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106870178A (en) * | 2015-12-14 | 2017-06-20 | 现代自动车株式会社 | Gradual braking device and its control method |
| CN106870178B (en) * | 2015-12-14 | 2021-04-30 | 现代自动车株式会社 | Braking force control device and control method thereof |
| CN105804827A (en) * | 2016-05-04 | 2016-07-27 | 哈尔滨工程大学 | Piezoelectrically-controlled pressure-intensified valve system |
| CN110185513A (en) * | 2019-07-01 | 2019-08-30 | 贵州大学 | A kind of electric-liquid type variable valve timing regulating device |
| CN111535894A (en) * | 2020-04-28 | 2020-08-14 | 一汽解放汽车有限公司 | Electric control hydraulic type air valve system and engine |
| CN111535894B (en) * | 2020-04-28 | 2021-02-19 | 一汽解放汽车有限公司 | Electric control hydraulic type air valve system and engine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2039892A1 (en) | 2009-03-25 |
| JPWO2008001699A1 (en) | 2009-11-26 |
| EP2039892A4 (en) | 2009-11-04 |
| EP2039892B1 (en) | 2012-03-21 |
| US20090199796A1 (en) | 2009-08-13 |
| KR101083613B1 (en) | 2011-11-16 |
| WO2008001699A1 (en) | 2008-01-03 |
| KR20090027649A (en) | 2009-03-17 |
| CN101473111B (en) | 2011-08-31 |
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