CN1882765A - Valve gear device of engine and method - Google Patents
Valve gear device of engine and method Download PDFInfo
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- CN1882765A CN1882765A CNA2004800344297A CN200480034429A CN1882765A CN 1882765 A CN1882765 A CN 1882765A CN A2004800344297 A CNA2004800344297 A CN A2004800344297A CN 200480034429 A CN200480034429 A CN 200480034429A CN 1882765 A CN1882765 A CN 1882765A
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- reciprocating piston
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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
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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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- Valve Device For Special Equipments (AREA)
Abstract
A valve operating apparatus for an internal combustion engine including: a housing (2); a reciprocating piston (1) residing wholly within the housing (2), the reciprocating piston (1) driving one or more poppet valves (7); a first fluid supply path and a first fluid drain path, each path being controllable to supply or drain fluid to/from a first reciprocating piston end (16); a second fluid supply path and a second fluid drain path, each path being controllable to supply or drain fluid to/from a second reciprocating piston end (17); wherein said reciprocating piston (1), in use, is driven between a first position and a second position by controlling said fluid in said supply and drain paths, thereby operating said one or more poppet valves (7), and wherein a connector (9) passes through an aperture (14) in said housing (2) to connect said reciprocating piston (1) to said one or more poppet valves (7), said reciprocating piston (1) in co-operation with an internal wall of the housing forming a seal to prevent substantial egress of fluid from the housing (2) through said aperture (14).
Description
Technical field
The present invention relates to the apparatus and method of a kind of operating internal-combustion engines suction valve and/or outlet valve.More specifically, the present invention relates to the connection set between operation equipment and valve, and the charging fluid actuating valve is used in operation during motor.
Background technique
The necessary aspect that the rising of the air inlet of Control of Automobile motor and/or exhaust (lifting) valve and timing are power operation.Traditional, drive the bar of air inlet or exhaust poppet valve and realize control by the mechanical system of using cam, and throttle valve is used to control the air stream that is fed to independent cylinder.Recently, be known that to have the cam that the rising that allows poppet valve can be regulated.But every kind of method has all caused loss in efficiency.
People have proposed the scheme of many treatment effeciency loss problems.For example, the someone has proposed to change the mechanical conceptual of rising to raise the efficiency of camshaft phase or poppet valve.Attempt to change the suggestion of hydraulic machinery of the rising of camshaft phase or valve in addition.The production meeting of these systems is very complicated and uneconomical.
Also the someone has proposed to use the electromagnetic scheme of solenoid-activated poppet valve, but the solenoid of sufficient size is big relatively, heavy and expensive, so it is unsuitable for mass production.
Also the someone proposes not have the hydraulic solution of camshaft, but before replace the trial of valve system's (valve train) cam and air throttle with hydraulic solution complexity make them be difficult to produce, and thereby uneconomical.The hydraulically powered poppet valve of Ti Chuing had both comprised usually that high pressure also comprised the low-pressure fluid supply before, and it need carry out great change to the motor of existing use camshaft.
Therefore, the repacking of this sampling device is expensive, because the proposal of prior art needs hydraulic system and the coaxial installation of the longitudinal axis of poppet valve, and therefore, existing cylinder head needs expensive change.Such scheme is considered to only be suitable for the purpose of combined structure motor usually.
Some existing schemes trend towards relying on the difference in surface area of the end of each driven plunger, the actuating valve on a direction of making a concerted effort of difference in surface area.By to the first end of piston accommodating fluid constantly, and alternately to the second end supply and exhaust fluid, when the second end does not have pressure, fluid pressure at the first end with small surface area causes that piston moves, and fluid is when being supplied in the second end, the fluid pressure that is increased by the bigger surface area of the second end and the bigger power that causes is returned piston.Therefore, this scheme that relates to the different table area is inefficient, because the power that the pressure by big end applies must overcome the constant power that the pressure by smaller end applies, this slows down system and has caused being difficult in the needed high-speed operation down of combustion engine.
For example, German patent application DE19826047A1 and International Application No. WO 03106820A1 disclose the hydraulic driving of poppet valve, and it passes through the constant pressure accommodating fluid of reciprocating piston to demarcate.The power of driven plunger can be approximated to be power=pressure * area, and this power depends on the difference in surface area of each end of piston.Must be faced with based on the method for driving of this operating principle and to be difficult to reach the desired high speed operation of internal-combustion engine.
Other existing scheme depends on a pistons end continuing accommodating fluid than low pressure, and to the other end with the higher pressure accommodating fluid with driven plunger.Higher pressure end by alternate supplies and bleed piston causes reciprocating motion of the pistons.But, caused so once more making system slow, and caused being difficult in the needed high-speed operation down of combustion engine.
In said system be disclosed in the electric hydaulic valve actuation apparatus system in German patent application DE19826047A1, international application 9207172 and the U.S. Pat 6321703 and have other efficiency.The problem that such electric hydaulic valve actuation device is run into comprises and is difficult to seal the fast moving part, especially poppet valve itself.Valve rod passes the place, position of the wall in the chamber that need be used for holding the fluid under the pressure action, must around the Sealing of bar extension in case the fluid stopping body leak in a large number from chamber around valve rod.Therefore, bar need seal in case the fluid stopping bulk diffusion around " high pressure " that bar extends.Certainly, high pressure sealing causes a large amount of frictional force, and for operating valve must overcome this frictional force, the fluid that therefore needs High Voltage more in valve mechanism is so that operated piston.Need stronger Sealing to leak out from chamber so successively around poppet valve to prevent charging fluid.Frictional force of being brought by high pressure sealing and operating valve and the bigger fluid pressure that needs have caused the degree of accuracy of the control of less poppet valve position, the less ability that variable control is provided and therefore lower overall engine efficiency, because the rising of poppet valve and regularly, be input into the air quantity of motor and therefore the thermodynamic efficiency of motor can not control with required validity.
Prior art does not provide simply, reliable especially effective, variable engine valve control system.The scheme complicated operation and the inefficiency of Ti Chuing before.The inefficiency of counteractive fluid pressure and the internal friction that caused by the high pressure sealing around valve rod have caused lower control accuracy and have finished the difficulty of high speed operation each other.At last, can not operate motor in the mode of full blast and retrain ability at required speed operation hydrovalve drive unit.Prior art also is unsuitable for reequiping the existing motor that comprises camshaft usually.
Because the feature of simple and easy, reliability and validity is for the important attribute such as the parts of complicated machineries such as motor, main purpose of the present invention provides the device that proposes with respect in (moreso than) prior art, has implemented the apparatus and method of the operating valve of one or more kinds in these features.
Any discussion of the file that comprises in this specification, device, action or knowledge is in order to explain context of the present invention.This will not be counted as before the priority date of this paper claim or the admitting of the prior art foundation on the same day or any material that the association area common practise is constituted.
Summary of the invention
First aspect present invention provides a kind of valve mechanism that is used for internal-combustion engine, and it comprises:
One shell;
The reciprocating piston of global existence within shell, this reciprocating piston drives one or more poppet valves;
First fluid feed path and first fluid vent pathway, each path be accommodating fluid to the first reciprocating piston end and end exhaust fluid from then on controllably;
The second fluid feed path and second fluid drain path, each path be accommodating fluid to the second reciprocating piston end and end exhaust fluid from then on controllably;
Wherein said reciprocating piston in use is driven between the primary importance and the second place by controlling the described fluid in described supply and the vent pathway, thereby operate described one or more poppet valve, and wherein a connection piece passes hole in the described shell described reciprocating piston being connected to described one or more poppet valve, and described reciprocating piston cooperates with outer casing inner wall and forms sealing in case the fluid stopping body passes described hole from shell flows out in a large number.
In an especially preferred embodiment, described hole is gone out in case the fluid stopping body passes described orifice flow from shell by at least a portion sealing of the outer surface of described reciprocating piston.
Existing hydraulic pressure valve mechanism need be in the sealing between the hydraulic fluid supply of the position that the poppet valve that moves and poppet valve are passed shell.Favourable, this device has been avoided such sealing.But described reciprocating piston self arrives the hole in the shell as Sealing to prevent charging fluid.
When reciprocating piston is used for preventing that fluid from passing the hole of outer shell outer wall and when leaking, because the friction that has been present between reciprocating piston and the shell significantly do not increase, so reduced interior friction in the hydraulic pressure valve mechanism.
Except reducing the quantity of required parts, the operation of valve mechanism of the present invention is more effective, and it is compared with existing systems and has less frictional force.Therefore, owing to increased the result of operating efficiency, can reach higher power operation speed.In addition, lower interior friction means that hydraulic system can operate to realize the action of poppet valve under lower fluid pressure.
In a particularly preferred embodiment according to the invention, the link bar is fixed to reciprocating piston and is connected to one or more poppet valves.The link bar can with the piston unitary moulding, therefore maybe can be the bar that passes the hole in the piston, and when reciprocating motion of the pistons, cause that itself and piston vertically move.Link preferably passes two holes in the shell, and its each side at piston so that drive two poppet valves, but also can be imagined an embodiment of passing the link in single hole.
In embodiment preferred of the present invention, described first reciprocating piston end and the described second reciprocating piston end have essentially identical surface area, owing to the fluid alternate supplies be discharged into pistons end reciprocating piston is moved.This preferred embodiment of the present invention depends on the pressure difference as the driving force on two direction of operating, and preferably the fluid of identical nominal pressure puts on each end of reciprocating piston successively.
When expectation control reciprocating piston, when for example slowing down, though the pressure of each end of reciprocating piston reaction each other, but the power (pressure) that puts on an end of reciprocating piston usually needn't overcome the opposite power in the other end, in existing system, have to overcome the opposite power in the other end by the lasting accommodating fluid in an end of piston is caused.In existing system, when driven plunger is resisted this constant pressure, need acting and higher pressure therefore to overcome the power that applies by this fluid.But, in less preferred embodiment of the present invention, at the fluid that is transported to the first reciprocating piston end be transported between the fluid of the second reciprocating piston end and have pressure difference.
Another embodiment of the present invention depends on the lasting supply of the fluid that is supplied to an end of reciprocating piston, and each end surface of this piston is long-pending to be different, so will cause reciprocating motion of the pistons to another pistons end alternate supplies fluid.In addition, owing to reduced whole efficiency, this embodiment is less preferred.
In another preferred embodiment of the present invention, open and close the supply of described fluid and vent pathway controlling flowing of described fluid, finish the described opening of each described fluid supply and vent pathway and close by the combination of one or more solenoid valves or rotary valve or described type control valve.These rapid response control valves have been strengthened the reactivity according to device of the present invention.
In a particularly preferred embodiment of the present, each described first fluid feed path, first fluid vent pathway, the second fluid feed path and second fluid drain path all have control valve, it is mobile to the fluid of described reciprocating piston first and second ends to operate four described control valves adjustings, therefore can control the also mobile of reciprocating piston so control one or more poppet valves.
Preferably, but each of four described control valves is independent operation.Preferably, each of four described control valves can be operated to have that close, that part is open or opened state.
With each supply and described one to one four control valves of vent pathway, permission is controlled widely for reciprocating piston and the mobile of poppet valve therefore, comprise ability, and acceleration and deceleration reciprocating piston are to prevent the valve collision or to reach other valve timing target with high speed operation reciprocating piston and poppet valve.
Another preferred embodiment of the present invention has high-pressure fluid container, and it is communicated with one or more described fluid feed path fluids.Because do not have the time lag of accumulated pressure, ato unit has difficulties, such situation may take place in the time of independent use pump, use container can help to pilot engine for this reason.In addition, any instantaneous interruption from the supply of pressure feeding mechanism can be compensated by high-pressure bottle.
The described fluid of controlling in described supply and the vent pathway can be finished by engine management system, and this system is also referred to as electric control device.Can be provided to this engine management system controller about the mass flow rate of temperature and pressure, humidity of the air and the input air of engine speed, required moment of torsion output, fluid and air and the information such as position of valve.The engine management system controller can be realized the variable rising of one or more poppet valves and the control of variable timing.
In a preferred embodiment, reciprocating piston is slowed down, collide on their pedestals separately to avoid described one or more poppet valve by the described fluid in described supply of control and the vent pathway.
In another preferred embodiment, when at idle state, reciprocating piston is offset to the precalculated position, thereby makes each described poppet valve be offset to the precalculated position.Can prevent departing from here device when reciprocating piston during at operable state acts on the reciprocating piston.
For example, can provide such as spring etc. and depart from device.In order to ensure overcoming any power that applies by such spring by the extra work of hydraulic system, when motor is in operation, spring can be at random by the position of pinning in a compressive state, only when motor is idle, this spring is not by pinning, so that reciprocating piston and poppet valve are biased to known location.
In addition, reciprocating piston can be a part hollow, therefore can provide a surface, and the power vertical at least one end of described reciprocating piston can act on this surface.
In the above-described embodiment, the connection between described reciprocating piston and described one or more poppet valve is realized by the link bar that is fixed on the reciprocating piston.Preferably, each connection to described one or more poppet valves allows described one or more poppet valves can center on their longitudinal axis rotation separately.
Brief Description Of Drawings
Will describe the preferred embodiments of the invention with reference to the accompanying drawings, it is not as the restriction of four corner of the present invention, wherein:
Fig. 1 shows the schematic representation of one embodiment of the invention; And
Fig. 1 a shows the schematic representation of second embodiment of the invention; And
Fig. 2 shows the sectional view of the preferred embodiment of the invention; And
The embodiment of Fig. 3 displayed map 2 is revolved the sectional view that turn 90 degrees; And
Fig. 4 shows the embodiment of solenoid valve; And
Fig. 5 shows another preferred embodiment of the present invention; And
Fig. 6 shows the sectional view of another embodiment of the present invention.
The embodiment of Fig. 7 presentation graphs 6 is revolved the sectional view that turn 90 degrees.
The explanation of preferred embodiment
In a preferred embodiment of the present invention, valve mechanism 31 (it is device that this paper also is referred to as valve) has formed the part of hydraulic system.The replaceable embodiment of hydraulic system schematically illustrates in Fig. 1 and 1a, and figure 5 illustrates the more detailed expression of the preferred embodiment of the invention.
With reference to figure 1,1a and 5, charging fluid is delivered to high-pressure bottle 22 from the storage tank 21 in low pressure such as pressure feeding mechanism 20 by engine-driven pump.When high-pressure bottle 22 was full of, the reduction valve 23 between pressure feeding mechanism 20 and high-pressure bottle 22 (this paper also is referred to as pressure controlled valve) was got back to storage tank 21 with any remaining fluid discharging.But, should be noted in the discussion above that high-pressure bottle 22 is not indispensable for the present invention as preferred.In addition, the high pressure distributor 29 that schematically shows among Fig. 1 can be set to the part of the flow control valve 30 of Fig. 2, or is the part of device self as valve mechanism 31 or valve.What should also be noted that is that single hydraulic system can be operated a plurality of valve mechanisms 31 or valve is a device.
With reference now to Fig. 2 and 3,, perhaps replacedly with reference to figure 6 and 7, they have represented to be used for the preferred embodiment of the valve mechanism 31 of internal-combustion engine, and the method that simplifies the operation of this device is as follows.Pressure fluid can be fed to first Room 11 from high-pressure bottle 22 or from pressure feeding mechanism 20 by first fluid feed path 3, and this first Room 11 is formed between the first end 16 and shell 2 of reciprocating piston 1.Close the first fluid vent pathway 5 that described first Room 11 is connected to low pressure vessel or storage tank 21, thereby the accumulation of pressure has caused hydraulic driving reciprocating piston 1 from the primary importance to the second place in first Room 11.Simultaneously, close the second fluid feed path 4 and open second fluid drain path 6, make any fluid in second Room 10 be discharged into storage tank 21 by second vent pathway 6.The motion of reciprocating piston 1 helps this discharging.
And reciprocating piston turns back to primary importance with similar process from the second place, wherein pressure fluid is by the second fluid feed path 4, be fed to second Room 10 from high-pressure bottle 22 or from pressure feeding mechanism 20, this second Room 10 is formed between the second end 17 and shell 2 of reciprocating piston 1.Close the first fluid vent pathway 6 that described second Room 10 is connected to storage tank 21, thereby and in second Room 10 accumulation pressure caused hydraulic driving reciprocating piston 1 from the second place to the primary importance.Simultaneously, close first fluid feed path 3 and open first fluid vent pathway 5, make fluid be discharged into storage tank 21 by first fluid vent pathway 5 from first Room 11.The motion of reciprocating piston 1 has helped this discharging once more.
Optional (not shown), first fluid feed path 3 and first fluid vent pathway 5 can be passed the independent port in the shell 2.With the same manner, the second fluid feed path 4 and vent pathway 6 also can be passed independent port.
The link bar 9 that moves through of reciprocating piston 1 drives one or more poppet valves 7.One or more poppet valves 7 are connected to link bar 9, connect 8 in shell 2 outsides.
Shown in Fig. 2,3,5,6 and 7, link bar 9 passes the hole 14 in the shell 2, and reciprocating piston 1 cooperates with shell 2 inwalls and formed sealing in case the fluid stopping body flows out by hole 14 in a large number from shell 2.Can flow out some fluids in a small amount under normal operation.
Shown in the preferred embodiment of the invention in, cooperate the described inwall of shell 2 and the sealing that provides is positioned near 14 places, described hole by described reciprocating piston 1, so, hole 14 basic sealings in case the fluid stopping body flow out by described hole 14 from shell 2.But, in a unshowned embodiment, reciprocating piston 1 non-essential in the hole 14 place's latch housings 2, but reciprocating piston 1 is simply at the position latch housing 2 that prevents to arrive from the fluid of chamber 10 and 11 hole 14.Therefore reciprocating piston 1 can not have the common constant diameter shown in figure, but can have the core than minor diameter, and itself and shell 2 form the annulus (annulus) of hollow.Interchangeable, in less preferred embodiment, reciprocating piston can only seal the chamber 10 or 11 that comprises charging fluid, does not have the pressure loss that causes because of the empty chamber of unsealing.
Because will there be frictional force in pore 14 what position in shell 2 between reciprocating piston 1 and the shell 2, reduce total internal friction of valve mechanism.In existing apparatus, reciprocating piston drives poppet valve by poppet valve being passed in the hole of hanging down the bottom of fluid chamber.Therefore, the high pressure sealing ability that needs the sealed hydraulic system under the high service speed at this.Because the such sealing between shell and the poppet valve will produce a large amount of extra interior frictions, it is very difficult reaching acceptable height operation.Opposite, the present invention has reduced the needs for such sealing, has reduced the interior friction of system greatly, and the to-and-fro motion under high speed that reciprocating piston 1 can be more prone to as required, has strengthened the efficient of whole motor.
By using the reciprocating piston 1 that matches with shell 2 inwalls to prevent that to form sealing fluid from passing hole 14 from shell 2 and flowing out in a large number, but minimum degree ground increases the frictional force that has existed, therefore with the existing apparatus comparison that comprises around the sealing of poppet valve, significant improvement is generally arranged.Native system can make reciprocating piston move more rapidly, can control more accurately.The operation of having guaranteed motor like this is more effective.
In addition, in the motor that comprises according to valve mechanism of the present invention, owing to need not be transported to the inefficient in essence throttle valve of engine air tolerance in order to control, thus improved the thermodynamic efficiency of motor.Instead, the accurate control that can realize owing to reduce internal friction make the variable control of reciprocating piston 1 and therefore poppet valve 7 variable control so that can realize.The variable rising of poppet valve 7 and variable timing have been controlled the amount of carrying air.In addition, the interior friction of minimizing can be more prone to reciprocating piston 1 as needs ground under high speed to-and-fro motion has also increased the efficient of whole motor and control to bigger operating range is provided.
The operation of above-mentioned working of an invention scheme can change owing to the accurate control that can access of the present invention.Reciprocating piston passes through to regulate the timing that opens and closes fluid passage, and/or can be accelerated and slow down by partially opening fluid passage.Reciprocating piston is slowed down reach so make the ability of poppet valve deceleration to guarantee to prevent the collision of poppet valve on the valve base seat.
In addition,, device is assembled on the motor car engine of existing scope, only needs countercylinder lid to do the change of minimum degree because the connection 8 of poppet valve 7 is manufactured in the outside of shell 2.Minimized like this from the required repacking work of standard cams system transition motor car engine, thereby the repacking that has reduced cost and made device is more economically with easy to implement.
The link bar 9 of the embodiment shown in the figure is a straight-bar, but the link of other shape can be suitable for specific motor, and described other shape such as U-shaped or asymmetric shape also may further reduce the change that countercylinder covers the needs of being done.Yet embodiment preferred has two radially relative link bars 9, and the radially relative hole 14 in the shell 2 is passed in the end of each link, can conceive less preferred embodiment and can have single link bar 9 and single hole 14.
In preferred embodiments, the connection 8 between link bar 9 and the poppet valve 7 can make each poppet valve 7 easily rotate around their longitudinal axis.Be desired like this, because during power operation, the turning effort of valve is for reducing the sedimentary accumulation on valve and the valve base seat.
Described device can be installed on the side of one or more poppet valves 7, but not coaxial, allows multiple poppet valve 7 to be connected to link bar 9.Simultaneously potential minimizing the quantity of valve mechanism, device according to the present invention with compare also the more cylinder head of low height of needs with the device of the coaxial reciprocating piston 1 of the longitudinal axis of poppet valve 7 bars.
The opening and closing of the first and second fluid supplies and vent pathway 3,4,5 and 6 are preferably operated by one or more quick acting control valves.In a preferred embodiment, each quick acting control valve is a solenoid valve, such as the example described in Fig. 4.The quick acting control valve can also be the valve system of rotary valve or combination.In another embodiment preferred, opening and closing separately, the control valve 24 of fluid passage is the type of sliding.
Relevant control valve can be arranged in high-pressure bottle 22 or storage tank 21, perhaps more preferably lays respectively in the first or second fluid supply or vent pathway 3,4,5 and 6.By controlling the first and second fluid supplies and the motion of controlling reciprocating piston 1 is opened, partially opens or closed to vent pathway 3,4,5 and 6.Successively, moving by the link bar one or more poppet valves 7 of 9 controls.
In a preferred embodiment, the control of control valve 24 is by electric control device 19, and this electric control device 19 is successively by engine management system (Engine Management System, EMS) control.Aspect this, sensor will provide information to electric control device 19 or EMS, and it comprises the information about the mass flow measurement of temperature, pressure and the humidity of the position of engine speed, driver's required torque (from accelerator pedal sensors), fluid temperature (F.T.) and pressure, valve, input air and input air.The sensor of the information that is used to provide such is generally used for modern engine management system.Also will detect information about hydraulic system, for example, will be by placing the sensor hydraulic fluid pressure of the position that is connected with the fluid feed path.And rising and the timing of information to regulate poppet valve that is provided by sensor will be provided for electric control device 19 or EMS.
Can be according to device of the present invention for the usefulness that increases engine efficiency, and the control of this device can be controlled the rising of poppet valve 7 and regularly in variable mode according to the needs of motor.Accurately control also makes poppet valve 7 stop stably and does not collide on separately the valve base seat.
In a preferred embodiment, when motor did not use, retaining spring 12 made reciprocating piston 1 turn back to predetermined known location, and therefore one or more poppet valves 7 turn back to predetermined known location.The advantage that has like this is the complexity that has further reduced required controlling component, because when piloting engine, needn't determine the initial position of poppet valve 7.Advantage with location or return spring 12 is that when motor is not worked poppet valve 7 maintained positions are known, thereby the starting position is known.Therefore, this method has been represented a kind of short-cut method of position of definite poppet valve 7, further simplified device and therefore increased its reliability, and it is easy to produce.In order to ensure the extra work that need not do by hydraulic system overcoming such spring 12, when motor at work, spring 12 can be at random by break 13 pinnings in the position of a compressive state, only when motor is not worked, not with its pinning.So that make reciprocating piston 1 and poppet valve 7 be biased to known location.
What those skilled in the art will recognize that is that this return spring 12 can be positioned at different positions.For example, as shown in the embodiment of Fig. 5, return spring 12 can be positioned at an end of the reciprocating piston 1 that is present in shell 2 inside.Interchangeable, as shown in the embodiment of Fig. 2, return spring 12 can be installed in the outside of shell 2, for example on poppet valve 7, or is connected to link bar 9 (not shown).
Because do not have the time lag of accumulated pressure, ato unit has difficulties, in the time of independent use pump, can produce such difficulty, the benefit with high-pressure bottle 22 of fluid is that motor can not have this kind and starts difficultly.In addition, can be from any instantaneous interruption of the supply of pressure feeding mechanism 20 by high-pressure bottle 22 compensation.As shown in fig. 1, container 22 can form the part in flow of pressurized loop, or as shown in Figure 1a, can undesiredly become the part of flow circuit in the common operation.
In a preferred embodiment, as shown in the embodiment of Fig. 7, reciprocating piston 1 can form the end 18 that has part hollow.Hole in the wall of hollow ends makes fluid enter into chamber 10 or 11 from fluid feed path separately, and described chamber 10 or 11 is formed between reciprocating piston 1 and the shell 2.Such device will significantly reduce reciprocating piston 1 and temporarily will be stuck in danger in the shell 2.But reciprocating piston needs not to be hollow, but can present any geometrical shape on the surface that is connected with associated chamber, and it can act on the direction of the longitudinal axis of reciprocating piston fluid, or even when reciprocating piston fully extends.
In an especially preferred embodiment, control four fluid passages (first and second supply and vent pathway 3,4,5 and 6) respectively, each path has their control valve 24, the closing, partially open or open of this control valve 24 of may command.The timing of control valve and condition influence the accurate control of reciprocating piston 1.The 1 of reciprocating piston 1 has identical calibration scale area with the second end 17, and by each pistons end 16 and 17 alternate supplies charging fluids are driven reciprocating piston 1.
By opening the control valve 24 that is positioned on the first fluid feed path 3, fluid is fed to the first end 16 that is formed at reciprocating piston 1 and first Room 11 between the shell 2.Close the first fluid vent pathway 5 that described first Room 11 is connected to low pressure vessel or storage tank 21, thereby and in first Room 11 accumulation pressure cause that hydraulic driving reciprocating piston 1 is from the primary importance to the second place.Simultaneously, can close the second fluid feed path 4 and open second fluid drain path 6, make any fluid in second Room 10 be discharged into storage tank 21 by second vent pathway 6.The motion of reciprocating piston 1 has helped this discharging.
Accurate and the variable control of reciprocating piston 1 motion can be obtained by the different operating of control valve 24.For example, slow down in order to make reciprocating piston 1, and poppet valve 7 is slowed down, finish at reciprocating piston 1 before its motion, can open or partially open the control valve 24 that is positioned on the second fluid feed path 4.Pressure to second Room, 10 accommodating fluids has applied the power that resists reciprocating piston 1 motion, makes its deceleration.Amount that valve is opened and timing are by electric control device 19 controls.Can defer to similar methods in the opposite direction driving reciprocating piston 1.
Important, slow down as required except making reciprocating piston, by regularly and the distance that can regulating piston moves of fluid supply.For example, in order to shorten the distance that moves by reciprocating piston 1 and therefore to shorten the distance that poppet valve 7 moves, rather than reciprocating piston 1 is slowed down, finish at reciprocating piston 1 before its motion, can fully open the control valve 24 that is positioned on the second fluid feed path 4, and finish at reciprocating piston 1 before its motion, can close the control valve 24 that is positioned on the first fluid feed path 3.Pressure to second Room, 10 accommodating fluids has applied the power that resists reciprocating piston 1 motion, and it is stopped.
When to first Room, 11 accommodating fluids, the degree of opening that is installed on the control valve 24 in the fluid feed path 3 will determine described chamber to fill quick degree, and therefore determine to drive the speed of reciprocating piston 1.
Each of four control valves 24 can be operated separately, but it is and other valve compounding practice that engine management system controller 19 has determined to open the degree of valve and the time control of each valve according to engine data.
Above-mentioned for direct control reciprocating piston speed, acceleration and deceleration and the ability of the distance that moves of reciprocating piston 1 directly determined the timing and the rising of poppet valve 7, and therefore determine amount to motor supply air.Owing to control can be adjustable and be constantly to change, and can respond very fast, electric control device can constantly be regulated the rising and the timing of poppet valve, guarantees to provide at any time the optimal air supply.Guaranteed the efficient of higher whole motor like this.
In a less preferred embodiment, can use the reciprocating piston 1 that on each end, has the different table area, and for example, charging fluid can constantly be fed to an end.In addition, in other less preferred embodiment, the lower pressure fluid can constantly be fed to piston one end, and the charging fluid of supply that replaces from the second end or discharging elevated pressures.These embodiments can need the hydraulic system different with the system shown in the accompanying drawing.Owing to avoided needs around the high pressure sealing ability of poppet valve for high speed operation, these embodiments still kept reduce in the advantage of friction.
Since can be several forms implement the present invention and do not depart from the purport of invention substantive characteristics, should be understood that above-mentioned embodiment is not restriction the present invention, but the explanation widely within the spirit and scope of the invention as defined by the appended claims.Different modifications and equality unit will be included within the spirit and scope of the invention.
Claims (13)
1. valve mechanism that is used for internal-combustion engine, it comprises:
Shell (2);
Reciprocating piston (1), its global existence are in described shell (2), and described reciprocating piston (1) drives one or more poppet valves (7);
First fluid feed path (3) and first fluid vent pathway (5), each described path controllable accommodating fluid to the first reciprocating piston end (16) and end exhaust fluid from then on;
The second fluid feed path (4) and second fluid drain path (6), each described path controllable accommodating fluid to the first reciprocating piston end (17) and end exhaust fluid from then on; Wherein said reciprocating piston (1) in use is driven between the primary importance and the second place by the described fluid in described supply of control and the vent pathway (3,4,5,6), thereby operate described one or more poppet valve (7), and wherein, link (9) passes hole (14) in the described shell (2) so that described reciprocating piston (1) is connected to described one or more poppet valve (7), and described reciprocating piston (1) cooperates the inwall of described shell to form sealing in case the fluid stopping body flows out by described hole (14) is a large amount of from described shell (2).
2. valve mechanism according to claim 1, wherein said hole (14) pass through to seal substantially to the described outer surface of the described reciprocating piston of small part (1), in case the fluid stopping body flows out by described hole (14) from described shell (2).
3. according to each described valve mechanism in the aforementioned claim, the link bar (9) that wherein is fixed to described reciprocating piston (1) is connected to described one or more poppet valve (7).
4. according to each described valve mechanism in the aforementioned claim, wherein said first reciprocating piston end (16) and the described second reciprocating piston end (17) have substantially the same surface area.
5. according to each described valve mechanism in the aforementioned claim, wherein said first fluid feed path (3), first fluid vent pathway (5), in the second fluid feed path (4) and second fluid drain path (6) each all has independent exercisable control valve (24), described control valve (24) can be operated to have and close, part open or opened state, operate four described control valves (24) and be adjusted to the described first and second reciprocating piston ends (16,17) fluid flow, therefore moving of described reciprocating piston (1) can be controlled, and therefore described one or more poppet valve (7) can be operated.
6. according to each described valve mechanism in the aforementioned claim, wherein high-pressure fluid container (22) is communicated with one or more described fluid feed path (3,4,5,6) fluid.
7. according to each described valve mechanism in the aforementioned claim, wherein the fluid in described supply and vent pathway (3,4,5,6) is by engine management system controller (19) control, described engine management system controller (19) is controlled the operation of described reciprocating piston (1), and therefore the variable rising of described one or more poppet valve (7) and variable timing can be controlled.
8. according to each described valve mechanism in the aforementioned claim, wherein described reciprocating piston (1) is slowed down, collide on their pedestals separately to avoid described one or more poppet valve (7) by the described fluid in described supply of control and the vent pathway (3,4,5,6).
9. according to each described valve mechanism in the aforementioned claim, wherein when in idle state, described reciprocating piston (1) is offset to the precalculated position, thereby make each described poppet valve (7) be offset to the precalculated position, and when described reciprocating piston (1) is in serviceability, prevent that the described device (12) that departs from from acting on the described reciprocating piston (1).
10. according to each described valve mechanism in the aforementioned claim, wherein said reciprocating piston (1) is a part hollow, described hollow (18) provides a surface, and vertical power can act on the described surface at least one end (16,17) of described reciprocating piston (1).
11. according to each described valve mechanism in the aforementioned claim, the described link (9) that wherein described reciprocating piston (1) is connected to described one or more poppet valve (7) allows each described poppet valve (7) around its longitudinal axis rotation.
12. a motor, it comprises according to each described valve mechanism in the aforementioned claim.
13. motor vehicle, it comprises according to each described valve mechanism in the aforementioned claim.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AU2003906627A AU2003906627A0 (en) | 2003-11-28 | Valve Operating Apparatus and Method for an Engine | |
| AU2003906627 | 2003-11-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1882765A true CN1882765A (en) | 2006-12-20 |
Family
ID=34437895
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2004800344297A Pending CN1882765A (en) | 2003-11-28 | 2004-11-29 | Valve gear device of engine and method |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US20070113804A1 (en) |
| EP (1) | EP1536107A1 (en) |
| JP (1) | JP2007533898A (en) |
| KR (1) | KR20060111612A (en) |
| CN (1) | CN1882765A (en) |
| BR (1) | BRPI0416410A (en) |
| CA (1) | CA2546813A1 (en) |
| WO (1) | WO2005052324A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103228878A (en) * | 2010-11-30 | 2013-07-31 | 瓦锡兰芬兰有限公司 | Device and method for operating a gas exchange valve of an internal combustion engine, cylinder head and method for upgrading an internal combustion engine |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2063075A1 (en) * | 2007-11-23 | 2009-05-27 | EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt | Fluid actuated valve mechanism |
| US7878166B2 (en) * | 2007-11-29 | 2011-02-01 | Perkins Engines Company Limited | Device and method for retaining a valve bridge |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4200067A (en) * | 1978-05-01 | 1980-04-29 | General Motors Corporation | Hydraulic valve actuator and fuel injection system |
| JPS59206606A (en) * | 1983-05-09 | 1984-11-22 | Mitsubishi Heavy Ind Ltd | Exhaust valve driving device of internal-combustion engine |
| DE3836725C1 (en) * | 1988-10-28 | 1989-12-21 | Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
| DE3911495C1 (en) * | 1989-04-08 | 1990-08-30 | Bayerische Motoren Werke Ag, 8000 Muenchen, De | Hydraulic valve actuation unit for piston engines |
| US4974495A (en) * | 1989-12-26 | 1990-12-04 | Magnavox Government And Industrial Electronics Company | Electro-hydraulic valve actuator |
| GB9022440D0 (en) | 1990-10-16 | 1990-11-28 | Lotus Car | Engine valve control apparatus |
| DE19826047A1 (en) | 1998-06-12 | 1999-12-16 | Bosch Gmbh Robert | Device for controlling a gas exchange valve for internal combustion engines |
| DE19931129A1 (en) * | 1998-07-11 | 2000-01-13 | Armin Stelzig | Timing gear for 4-stroke combustion engines has valve lifter connected to hydraulic control piston, and two cylinder pressure chambers connected to pressure source/reducer via rotary slide valves |
| WO2000012895A2 (en) * | 1998-08-26 | 2000-03-09 | Diesel Engine Retarders, Inc. | Valve seating control device with variable area orifice |
| JP2000310104A (en) * | 1999-04-28 | 2000-11-07 | Isuzu Motors Ltd | Valve system for engine |
| EP1212518B1 (en) * | 1999-09-16 | 2010-01-06 | Diesel Engine Retarders, Inc. | Method and apparatus for valve seating velocity control |
| US6505584B2 (en) * | 2000-12-20 | 2003-01-14 | Visteon Global Technologies, Inc. | Variable engine valve control system |
| US6827050B2 (en) * | 2001-12-21 | 2004-12-07 | Caterpillar Inc | Fluid control valve actuating system |
| US6772742B2 (en) * | 2002-03-01 | 2004-08-10 | International Engine Intellectual Property Company, Llc | Method and apparatus for flexibly regulating internal combustion engine valve flow |
| DE10226254A1 (en) | 2002-06-13 | 2003-12-24 | Bosch Gmbh Robert | Hydraulically controlled actuator for actuating an exhaust gas exchange valve of an internal combustion engine |
| US6899068B2 (en) * | 2002-09-30 | 2005-05-31 | Caterpillar Inc | Hydraulic valve actuation system |
| US6959673B2 (en) * | 2003-04-02 | 2005-11-01 | General Motors Corporation | Engine valve actuator assembly with dual automatic regulation |
-
2004
- 2004-11-26 EP EP04028150A patent/EP1536107A1/en not_active Withdrawn
- 2004-11-29 BR BRPI0416410-5A patent/BRPI0416410A/en not_active Application Discontinuation
- 2004-11-29 US US10/581,241 patent/US20070113804A1/en not_active Abandoned
- 2004-11-29 CN CNA2004800344297A patent/CN1882765A/en active Pending
- 2004-11-29 CA CA002546813A patent/CA2546813A1/en not_active Abandoned
- 2004-11-29 KR KR1020067012575A patent/KR20060111612A/en not_active Withdrawn
- 2004-11-29 JP JP2006540100A patent/JP2007533898A/en active Pending
- 2004-11-29 WO PCT/AU2004/001668 patent/WO2005052324A1/en not_active Ceased
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103228878A (en) * | 2010-11-30 | 2013-07-31 | 瓦锡兰芬兰有限公司 | Device and method for operating a gas exchange valve of an internal combustion engine, cylinder head and method for upgrading an internal combustion engine |
| CN103228878B (en) * | 2010-11-30 | 2015-06-24 | 瓦锡兰芬兰有限公司 | Device and method for operating a gas exchange valve of an internal combustion engine, cylinder head and method for upgrading an internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20060111612A (en) | 2006-10-27 |
| US20070113804A1 (en) | 2007-05-24 |
| CA2546813A1 (en) | 2005-06-09 |
| WO2005052324A1 (en) | 2005-06-09 |
| BRPI0416410A (en) | 2007-01-09 |
| JP2007533898A (en) | 2007-11-22 |
| EP1536107A1 (en) | 2005-06-01 |
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