CN102606251A - Variable valve actuator - Google Patents
Variable valve actuator Download PDFInfo
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- CN102606251A CN102606251A CN2012100951845A CN201210095184A CN102606251A CN 102606251 A CN102606251 A CN 102606251A CN 2012100951845 A CN2012100951845 A CN 2012100951845A CN 201210095184 A CN201210095184 A CN 201210095184A CN 102606251 A CN102606251 A CN 102606251A
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Abstract
The invention discloses an actuator, whichis divided into a hydraulic control loop portion and a spring mechanical system portion and comprises a shell, an actuating cylinder, an actuating piston, a first fluid space, a second fluid space, a first piston rod, a second piston rod, a fluid bypass, a first spring system, a second spring system, a first flowing mechanism and a second flowing system. The shell is provided with an upper port and a lower port, the actuating cylinder is arranged in the shell, the actuating piston in the cylinder can move along a longitudinal axis, the first piston rod is connected to a first surface of the actuating piston, the second piston rod is connected to a second surface of the actuating piston, the first spring system is connected with the first piston rod and eccentrically presses the actuating piston along a second direction, and the second spring system eccentrically presses the actuating piston along a first direction. The invention further discloses two other actuators. The actuator has the advantages that the lift of a valve is variable, energy consumption is low, response speed is fast, valve crash speed is slow, control is simple and reliable, and the like.
Description
Technical field
The correlation technique and the system that present invention relates in general to actuator and be used to control this actuator, and particularly, relate to the actuator that independent lift (or stroke or stroke) and control in correct time can be provided with minimal energy consumption.
Background technique
Can adopt various systems to come the effectively correct time and the lift of control engine valve, improve performance, fuel economy, injection and other characteristics of motor.According to the device or the actuator of control, these systems can be divided into (electrohydraulic) machinery, electric liquid and dynamo-electric (being sometimes referred to as electromagnetism) form.According to the scope of control, can be divided into the form of lift range variable and correct time, VVT and lift range variable.They also can be divided into has cam (cam-based) or indirectly-acting and does not have cam or direct acting form.
Under the situation of the system that cam is arranged, keep Traditional engine camming and modification a little, to control valve timing and/or valve lift indirectly.In no camming, the Traditional engine camming is replaced with the electric liquid or the electromechanical actuator that directly drive each engine valve fully.Although there is camming wideer controllability is not provided, stop using (deactivation) of cylinder and valve for example, and have better fuel economy thus, all existing variable automobile valve systems of producing all have cam.
The problem of dynamo-electric no camming comprises and soft landing (soft-landing), the requirement of high electric power, difficulty that scarce capacity is relevant, perhaps restive lift and handle the limited in one's ability of cylinder air pressure high and/or variation.Electricity liquid does not have camming and can overcome such problem usually, but there is the problem of self really in it, and for example performance under high engine speed and design or control are complicated, cause the conflict between response time and the flow.For 6,000 to 7, move under the 000rpm, actuator must at first quicken geared-down engine valve then on the scope at 8mm in 2.5 to 3 milliseconds time.Engine valve must be advanced at the peak velocity of about 5 meter per seconds.These have required to have reached the limit of traditional electrical liquid technology.
An approach that overcomes this performance limitations is, it is the same to be similar to Mechatronic Systems, in electrohydraulic system, adds a pair of relative spring (opposing springs), and the moving-mass of itself and system comes together to produce spring-mass resonance or oscillation system.Under static state, this relative spring is arranged on engine valve between the endpoint location of this valve between two parties, promptly opens and closes between the position.In order to keep engine valve on an endpoint location, system must have certain locking framework, resists from this clean return force to spring, and it has accumulated potential energy on any one of two end points.When from an endpoint location when another end points position row is advanced, engine valve is at first driven by the spring return force and quickens, and by the potential energy of spring storage power is provided, up to the mid point at stroke, it reaches top speed and has corresponding kinetic energy herein; The return force of its antagonistic spring keeps travelling forward then, by kinetic energy power is provided, and up to the other end, its speed drops to zero herein, and corresponding kinetic energy changes the potential energy of spring storage into.
With regard to the working principle that it is known, spring mass system this in the transformation of energy aspect very effectively and very reliable.A lot of technological development have been to design effectively and reliable locking-releasing mechanism; It can remain on its opening and closing position with engine valve; Discharge as requested; Increase the engine cylinder air pressure that additional-energy comes friction compensation and alterable height, and resistance ceases unnecessary energy before it lands on the other end.As discussed above, exist and dynamo-electric or the relevant difficulty of electromagnetic locking-releasing device.Also had the people lock at electric liquid-carried out effort aspect the exploitation of releasing device.
The United States Patent(USP) No. 4 that belongs to Daimler Chrysler (DaimlerChrysler); 930,464 what disclosed is a kind of electric liquid actuator, and it comprises two rod oil cylinders (double-ended rod cylinder), a pair of relative spring and bypass; Said relative spring is tending towards piston is arranged at the centre of oil cylinder; Said bypass is two cylinder chamber of short circuit on most of stroke, and like this, hydraulic jack is not wasted energy.When engine valve during in closed position; Bypass is inoperative; Piston is divided into bigger unlatching side room and the less side room of closing with oil cylinder; And when opening the side room and closing the side room and stand high-voltage power supply and low pressure source respectively, engine valve can lock, this be since on piston the generation differential pressure opposite with return spring power.When engine valve was in the enable possition, piston was divided into bigger side room and the less unlatching side room closed with oil cylinder, and closed the side room and high-voltage power supply is stood in less unlatching side room respectively and low pressure source can lock engine valve through bigger.
No matter in the enable possition still in closed position; Discharge the pressure in the big chamber through opening the two logical valves (2-way trigger valve) that trigger simply; Eliminate the differential pressure on the piston thus, trigger the swing power of spring mass system, come the release engine valve.This Twoway valves must cut out before stroke finishes once more very apace, thereby big chamber pressure can be elevated to enough greatly with lock piston fast, and therefore engine valve is in its new endpoint location.This structure also has the two logical valves that advance, to introduce extra driving force on the top end at valve rod between the unlatching stroke.
Aforementioned system has several potential problems.This two logical valve that triggers must be no more than in very short cycle of 3 milliseconds with in good time mode opening and closing.This two logical valve that advances is driven by the differential pressure in the alleged stroke space of two cylinder chamber or inventor, and has too many time lag and hydraulic pressure transient wave advancing between valve and the cylinder chamber potentially.Near each stroke finished, bigger cylinder chamber must come backfill through the fluid of being supplied with by a restrictor, and this requires restrictor member that sizable opening size is arranged.On the other hand, in the beginning of each stroke, this two logical valve that triggers must discharge the pressure of chamber greatly, and this big chamber is communicated with high-pressure fluid source through same restrictor.Closing between stroke, up to very near the end of stroke do not have effective method increase other hydraulic pressure can, if there is too big frictional loss, this will be a problem.Equally, this invention has no idea to regulate its lift.
U. S. Patent 5,595,148,5,765,515,5,809,950,6,167,853,6,491,007 and 6,601, also belonged to Daimler Chrysler No. 552, these patents have disclosed U. S. Patent 4,930, the improvement of No. 464 instructions.Disclosed the U. S. Patent 5,595,148,5,765,515,5,809,950 and 6,167 of various hydraulic spring grease cup devices, 853 purport be open stroke begin increase other hydraulic pressure can, overcome the air pressure of engine cylinder.A shortcoming of hydraulic spring grease cup is that its pressure descends rapidly in case engine valve movement begins.
At U. S. Patent 6,601, in No. 552, a kind of compress control method is provided, in the hydraulic spring grease cup device, keeping constant pressure on the variable part of valve lift, yet this requires selector valve in 1 millisecond very short cycle, between two positions, to switch.In addition, this system comprises two pressure springs: first spring and second spring are tending towards respectively the engine air door assembly is driven into and close and the enable possition.Connect hydraulic spring grease cup device and the second pressure spring entity.During unlatching stroke very major part; Although there is the motion of valve; It is designed to attempt to keep pressure in the hydraulic spring grease cup; And the air pressure and other frictional force that therefore provide other driving force to overcome engine cylinder cause the increase of the net flow body volume in the hydraulic spring grease cup device and the increase of the effective preload in second pressure spring, and this is because due to the equilibrium of forces between hydraulic spring grease cup and the pressure spring.In valve-closing stroke subsequently, engine valve may not be pushed to fully always and be closed, and this is owing to due to the higher resistance of second pressure spring.
The total problem of all patent family applications of invention is to open or close two switch motions that stroke must have control valve for each.Another common problem is the length that has the actuator of two pressure springs that separated by hydraulic spring grease cup.When spring rows is listed on the same axis, like U. S. Patent 5,809, disclosed for No. 950, total height can be extraordinary.In other patent of this patent family application, spring is not arranged on the linear axis, and what replace is crooked at the hydraulic spring grease cup place, but fluid inertia, frictional loss and transient state hydraulic pressure ripple and delay can become serious problems.Another common problem is only close stroke through the swing energy drives, but the existence of actual frictional loss can cause serious threat for normal operation.For release or releasing mechanism, some embodiments adopt threeway to trigger the cell supercharging that valve makes oil cylinder momently, with two lip-deep pressure of equalizing piston, and are reduced to the differential pressure on the piston zero from the pressure that is suitable for locking.Trigger valve and also must in the very short time cycle, realize two actions.
U. S. Patent 5,248 has disclosed another kind of electric liquid actuator No. 123; It comprises two rod oil cylinders, is tending towards piston is arranged on the middle a pair of relative spring of cylinder between two parties; And the bypass of two cylinder chamber of short circuit on most of stroke, like this, hydraulic jack is not wasted energy.Very similar with the patent of the Daimler Chrysler that is quoted, it has the bigger hydraulic jack chamber that always is connected to high voltage supply.Yet different with Daimler Chrysler is that it adopts the five-way two-position valve to start the valve switching, and each stroke is only required a valve events.This valve has five external hydraulic line: low pressure source pipeline, high-voltage power supply pipeline, constant high-pressure output tube line and two export pipelines with corresponding and switchable force value.Constant high-pressure output tube line is connected with the bigger chamber of oil cylinder.Two other export pipelines are connected to two ends of oil cylinder, and optionally are communicated with the less chamber of oil cylinder.With Daimler Chrysler discloses very similarly be, its stroke begin do not have effective ways increase hydraulic pressure can, with compensation engine cylinder air pressure and frictional loss.It can not control the lift of valve.
Chinese patent ZL200680021728.6 number (and corresponding U. S. Patent 7,302,920,7; 194,991 and 7,156; No. 058 and Indian patent application SV/AK/218/DELNP/2008 number) disclosed another kind of electric liquid actuator, control of two-stage lift and control in stepless correct time can be provided.This technology also adopts dual spring pendulum and electric liquid locking-releasing device, similar techniques relatively before, and it has more effective locking-releasing device.
No. 200680028252.9 (and corresponding U. S. Patents 7,290,509,7 of one Chinese patent application; 213,549 and 7,370; No. 615) disclosed another kind of electric liquid actuator; This technology also adopts dual spring pendulum and electric liquid locking-releasing device, and except intrinsic stepless correct time control ability, it can also carry out stepless lift control.
Summary of the invention
The technical problem that the present invention mainly solves provides a kind of variable valve actuator, possesses variable valve lift, low energy consumption, and high response speed, valve crash speed is little, controls characteristics such as simple and reliable.
For solving the problems of the technologies described above, the technological scheme that the present invention adopts is: a kind of actuator is provided, comprises:
Housing has upper end-hole and lower end mouth;
Actuation-cylinder in said housing, first direction longitudinally or second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is connected with said first piston bar, along the said power piston of second direction bias voltage; And have at least two original states, the initial bias voltage power of at least two different sizes is provided to said power piston;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said first piston bar, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part.
In preferred embodiment of the present invention; Said first spring system; Comprise first driving spring, spring seat, spring control cylinder block and plunger, said first driving spring is placed oneself in the midst of between said spring seat and the said spring control cylinder block, and said spring seat is connected with said first piston bar; In the said spring control cylinder block oil pocket is arranged, said plunger has a runner; Said housing comprises a cavity and its enable port; Said first spring system is installed in the said cavity; Runner is communicated with said oil pocket and said its enable port in the said plunger; Said spring control cylinder block can vertically move in said cavity with respect to said housing, with the decrement along said first driving spring of vertical change.
Another technological scheme that the present invention adopts is: a kind of actuator is provided, comprises:
Housing has upper end-hole and lower end mouth, and said upper end-hole also comprises first upper end-hole and second upper end-hole;
Actuation-cylinder in said housing, first direction longitudinally or second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is along the said power piston of second direction bias voltage;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said second piston rod, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said first piston bar to be comprising first piston bar first neck, first piston bar first shaft shoulder, first piston bar second neck and first piston bar second shaft shoulder near the order of said power piston, its each all have outside dimensions;
Said first-class actuation mechanism comprises first control hole with Inner Dimension;
The Inner Dimension of said first control hole is a bit larger tham the outside dimensions of said first piston bar first shaft shoulder and said first piston bar second shaft shoulder; And significantly greater than the outside dimensions of said first piston bar first neck and said first piston bar second neck; And when said fluid bypass is opened basically; Said first piston bar first shaft shoulder and said first control hole vertically overlap, and said first fluid space and said upper end-hole are cut off;
When the first surface of said power piston to the approaching terminal stage of the first end of said actuation-cylinder; Said first piston bar first shaft shoulder is the part of said first control hole of overlapping between said first upper end-hole and said second upper end-hole vertically, to cut off first upper end-hole and second upper end-hole.
In preferred embodiment of the present invention; The outside dimensions of the said first piston bar second shoulder axle is less than the outside dimensions of the said first piston bar first shoulder axle; Accordingly; Said first control hole comprises first portion and the second portion that matches with said first piston bar first shoulder axle and the said first piston bar second shoulder axle respectively; But the Inner Dimension of said first portion and the said first piston bar first shoulder axle slide relative ground are complementary, but the outside dimensions slide relative ground of the Inner Dimension of said second portion and the said first piston bar second shoulder axle is complementary.
In preferred embodiment of the present invention, on the end face of said first piston bar first shaft shoulder near said first piston bar second neck at least one first segment chute is arranged.
In preferred embodiment of the present invention; When said actuator also comprises first buffer with the first end of advancing at said power piston near said actuation-cylinder; The speed that suppresses said power piston; Said actuator also comprises first hydraulic power that is communicated in said upper end-hole, and said first buffer is positioned on the runner that is communicated with said second upper end-hole and said first hydraulic power.
In preferred embodiment of the present invention, said first buffer comprises first one-way valve, first segment head piece and first relief valve of parallel connection.
In preferred embodiment of the present invention, said first relief valve is adjustable relief valve.
Another technological scheme that the present invention adopts is: a kind of actuator is provided, comprises:
Housing has upper end-hole and lower end mouth, and said lower end mouth also comprises first lower end mouth and second lower end mouth;
Actuation-cylinder in said housing, first direction longitudinally or second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is along the said power piston of second direction bias voltage;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said second piston rod, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said second piston rod to be comprising second piston rod, first neck, second piston rod, first shaft shoulder, second piston rod, second neck and second piston rod, second shaft shoulder near the order of said power piston, its each all have outside dimensions;
The said second mobile mechanism comprises second control hole with Inner Dimension;
The Inner Dimension of said second control hole is a bit larger tham the outside dimensions of said second piston rod, first shaft shoulder and said second piston rod, second shaft shoulder; And significantly greater than the outside dimensions of said second piston rod, first neck and said second piston rod, second neck; And when said fluid bypass is opened basically; Said second piston rod, first shaft shoulder and said first control hole vertically overlap, and said second fluid space and said lower end mouth are cut off;
When the second surface of said power piston to the approaching terminal stage of the second end of said actuation-cylinder; Said second piston rod, first shaft shoulder is the part of said second control hole of overlapping between first lower end mouth and second lower end mouth vertically, to cut off said first lower end mouth and said second lower end mouth.
In preferred embodiment of the present invention, on the end face of said second piston rod, first shaft shoulder near second piston rod, second neck at least one second throttling groove is arranged.
In preferred embodiment of the present invention; When said actuator also comprises second buffer with the second end of advancing at said power piston near said actuation-cylinder; The speed that suppresses said power piston; Said actuator also comprises second hydraulic power that is communicated in said lower end mouth, and said second buffer is positioned on the runner that is communicated with said second lower end mouth and said second hydraulic power.
In preferred embodiment of the present invention, said second buffer comprises second one-way valve, second restriction and second relief valve of parallel connection.
The invention has the beneficial effects as follows: variable valve actuator of the present invention, possess variable valve lift, low energy consumption, high response speed, valve crash speed is little, controls characteristics such as simple and reliable.Especially, (1) has comprised unique last driving spring control structure, compact structure, and it is reliable and stable to lead, and has shortened the first piston pole length and has reduced whole actuator movements part quality, has improved actuator movements speed, has reduced energy consumption; (2) comprise effectively release and Cushioning Design, solved the contradiction on 26S Proteasome Structure and Function between release and the buffering.
Description of drawings
Fig. 1 is the structural representation of little lift original state one preferred embodiment of variable valve actuator valve of the present invention;
Fig. 2 is the structural representation that the little lift valve operating of variable valve actuator valve shown in Figure 1 is opened to maximum rating;
Fig. 3 is the structural representation of variable valve actuator valve high-lift original state shown in Figure 1;
Fig. 4 is the structural representation that variable valve actuator valve high-lift valve shown in Figure 1 is opened to maximum rating;
Fig. 5 is the another kind of embodiment's of a variable valve actuator of the present invention structural representation;
The mark of each parts is following in the accompanying drawing:
The 110-longitudinal axis; The 200-housing; 211-first upper end-hole; 212-second upper end-hole; 221-first lower end mouth; 222-second lower end mouth; The 230-actuation-cylinder; The 231-first end; The 232-the second end; The 240-fluid bypass; 241-first edge; 242-second edge; The 250-cavity; 251-first confined planes; 252-second confined planes; The 260-its enable port; 271-first control hole; 272-second control hole; The 300-power piston; The 310-first surface; The 320-second surface; 410-first piston bar; 411-first piston bar first neck; The 412-first piston bar first shoulder axle; 413-first piston bar second neck; The 414-first piston bar second shoulder axle; 4121-first segment chute; 420-second piston rod; 421-second piston rod first neck; The 422-second piston rod first shoulder axle; 423-second piston rod second neck; The 424-second piston rod second shoulder axle; 4221-second throttling groove; The 511-spring seat; 512-first driving spring; 513-spring control cylinder block; 5131-cylinder body upper surface; 5132-cylinder body lower surface; The 5133-oil pocket; The 514-plunger; The 5141-runner; The 515-semi-ring; The 521-cotter seat; 522-second driving spring; The 523-cylinder body; 524-valve guide; 611-first hydraulic power; 612; 612 '-the first one-way valve; 613; 6121-first segment head piece; 614-first relief valve; 621-second hydraulic power; 622-second one-way valve; 623; 6241-second restriction; 624; 624 '-the second relief valve; The 700-valve; The 710-engine valve head; 720; Engine valve seat; The 730-valve stem; 800-primer fluid potential source.
Embodiment
Below in conjunction with accompanying drawing preferred embodiment of the present invention is set forth in detail, thereby protection scope of the present invention is made more explicit defining so that advantage of the present invention and characteristic can be easier to it will be appreciated by those skilled in the art that.
See also Fig. 1 and Fig. 3, the embodiment of the invention comprises:
A kind of actuator; Comprise: housing 200; In this housing; Along longitudinal axis 110 and along second direction (in the accompanying drawings from the top to the direction of bottom), have its enable port 260, cavity 250, first control hole 271, first upper end-hole 211, second upper end-hole 212, actuation-cylinder 230, fluid bypass 240, second lower end mouth 222, first lower end mouth 221, second control hole 272; And be arranged on 250 li of cavitys first spring system (mark), be arranged on first piston bar 410 in first control hole 271, be arranged on power piston 300 in actuation-cylinder 230 and the fluid bypass 240, be arranged on second piston rod 420 in second control hole 272; And second spring system (mark), engine valve 700; And second hydraulic power 621 that is connected with lower end mouth with first hydraulic power 611 that primer fluid potential source 800 that its enable port 260 is communicated with is connected with upper end-hole.Among Fig. 1, first hydraulic power 611 and second hydraulic power 621 controllably link to each other with oil supply system through hydraulic control valve (such as rapid reversal valve, not showing among Fig. 1), between high (PH) low (PL) of system presses, switch.Under the working condition of Fig. 1, first hydraulic power 611 and second hydraulic power 621 are respectively under system low-voltage (PL) and system high pressure (PH).System low-voltage (PL) can be one and pass through back pressure system low pressure control, more stable, also possibly be the low pressure of directly leading to fuel tank.Primer fluid potential source 800 is under spring pilot pressure (PS); Spring pilot pressure (PS) can pass through certain hydraulic control valve (showing among Fig. 1) and controllably link to each other with oil supply system, and spring pilot pressure (PS) also can switch between system high pressure (PH) or low (PL) pressure.In Fig. 1, spring pilot pressure (PS) is got a low value, is not enough to that spring is controlled cylinder block 513 and drives along second direction.
First upper end-hole 211 and second upper end-hole 212 can be commonly referred to as upper end-hole, and upper end-hole will comprise in first upper end-hole 211 and second upper end-hole 212 at least; First lower end mouth 221 and second lower end mouth 222 can be commonly referred to as lower end mouth, and lower end mouth will comprise in first lower end mouth 221 and second lower end mouth 222 at least.
Said first piston bar 410 with near the order of said power piston 300 promptly along comprising first piston bar first neck 411, first piston bar first shaft shoulder 412, first piston bar second neck 413 and first piston bar second shaft shoulder 414 on the first direction direction of bottom to top (in the accompanying drawings from) successively; Form first-class actuation mechanism with first control hole 271.The Inner Dimension of said first control hole 271 is a bit larger tham the outside dimensions of said first piston bar first shaft shoulder 412 and said first piston bar second shaft shoulder 414, and significantly greater than the outside dimensions of said first piston bar first neck 411 and said first piston bar second neck 413.
Embodiment shown in Fig. 1, first piston bar first shaft shoulder 412 is identical with the outside dimensions of second shaft shoulder 414, and corresponding first control hole 271 can only have an outside dimensions; Further preferred situation: the outside dimensions of the said first piston bar second shoulder axle 414 is less than the outside dimensions of the said first piston bar first shoulder axle 412; Accordingly; Said first control hole 271 comprises first portion and the second portion that matches with said first piston bar first shoulder axle 412 and the said first piston bar second shoulder axle 414 respectively; But the Inner Dimension of said first portion and the said first piston bar first shoulder axle 412 slide relative ground are complementary, but the outside dimensions slide relative ground of the Inner Dimension of said second portion and the said first piston bar second shoulder axle 414 is complementary.
Said second piston rod 420 with near the order of said power piston 300 promptly along comprising second piston rod, first neck 421, second piston rod, first shaft shoulder 422, second piston rod, second neck 423 and second piston rod, second shaft shoulder 424 on the second direction direction of top to bottom (in the accompanying drawings from) successively; Form the second mobile mechanism with second control hole 271.The Inner Dimension of said second control hole 271 is a bit larger tham the outside dimensions of said second piston rod, first shaft shoulder 422 and said second piston rod, second shaft shoulder 424, and significantly greater than the outside dimensions of said second piston rod, first neck 421 and said second piston rod, second neck 423.
Similar with first-class actuation mechanism: the outside dimensions of second piston rod, first shaft shoulder 422 and second shaft shoulder 424 is identical, also can be the outside dimensions of the outside dimensions of the said first piston bar second shoulder axle 424 less than the said first piston bar first shoulder axle 422.
In actuation-cylinder 230, have the first fluid space that limits actuation-cylinder first end 231 and power piston first surface 310 and limit second fluid space actuation-cylinder the second end 232 and power piston second surface 320.
Be between actuation-cylinder 230, the first edges 241 and second edge 242 fluid bypass 240 to be arranged between first end 231 and the second end 232, fluid bypass 240 provides the hydraulic pressure short circuit on big minister's degree of actuation-cylinder 230.Through this hydraulic pressure short circuit, fluid can flow with very low basically resistance between the first fluid space and second fluid space, and whole actuation-cylinder 230 is in the pressure that equates basically.When power piston 300 first surfaces 310 surpass bypass first edge 241 on first direction, when perhaps power piston 300 second surfaces 320 surpassed bypass second edge 242 on second direction, the hydraulic pressure short circuit was all inoperative.Longitudinal space between bypass first edge 241 and the actuation-cylinder first end 231 is first effective oil pressure chamber, and its length is the L1 among Fig. 1.Longitudinal space between bypass second edge 242 and the actuation-cylinder the second end 232 is second effective oil pressure chamber, when power piston 300 not with first effective oil pressure chamber and second effective oil pressure chamber in during one of any joint, fluid bypass 240 is effective.
Said first spring system comprises first driving spring 512, spring seat 511, spring control cylinder block 513 and plunger 514; Said first driving spring 512 is placed oneself in the midst of between said spring seat 511 and the spring control cylinder block 513; Said spring seat 511 is connected with said first piston bar 410; Between can be fixing through semi-ring 515, in the said spring control cylinder block 513 oil pocket 5133 is arranged, said plunger 514 is fixedly attached on the said housing 200 and extends in the said oil pocket 5133; Plunger 514 also can be same one in mechanism with housing 200, has a runner 5141 to be communicated with said oil pocket 5133 and its enable port 260 in the said plunger 514.Driving spring 512 overheads and concentric with first piston bar 410 are gone up in design in this real example, and runner 5141 is arranged in the plunger 514, and the to-and-fro motion when going up driving spring 512 for 513 compressions of spring control cylinder block realizes guiding, joins oil.Have the following advantages: avoid driving spring 512 and first piston bar 410 not only concentric but also when axial overlap is arranged, because of the first piston bar 410 that spring control gear (spring seat 511) and the effective working stroke of spring cause long; Shortened the length of first piston bar 410, corresponding the reducing of first piston bar 410 diameters ability, light weight has effectively reduced whole actuator movements part quality, has improved actuator movements speed, has reduced energy consumption.Last driving spring control structure is compact, and it is reliable and stable to lead, and avoids driving spring 512 when compression, to produce lateral force.Adopt the two ends and the housing supporting structure of piston rod; Obtain maximum effective bearing length when making piston rod movement, reduced the side direction moment on the piston rod to greatest extent, improved the stability of actuator movements.
If the enclosed cavity cavity 250 not necessarily resembles among Fig. 1 in fact produces the image of feeling suffocated in order to prevent when spring control cylinder block 513 moves, should add the passage (representing among Fig. 1) of an assurance cavity 250 and ambient air circulation.The top of housing 200 in addition can be structurally not with housing 200 other partial continuous or directly continuously (expression among Fig. 1), the top of main housing 200 and other part do not have relative movement.
Said second spring system comprises cotter seat 521, second driving spring 522, valve guide 524 and cylinder body 523; Cotter seat 521 is connected with valve stem 730 1 ends; Valve stem 730 the other ends are connected with engine valve head 710; Said cylinder body 523 is between cotter seat 521 and engine valve head 710; On the valve guide 524 suit cylinder bodies, valve stem 730 passes from valve guide cover, and said second driving spring 522 is sleeved on the valve stem 730 and contacts with cotter seat 521 with cylinder body 523 simultaneously.
Said first upper end-hole 211 directly is communicated with first hydraulic power 611 by runner; Second upper end-hole 212 is communicated with first hydraulic power 611 through first buffer again, and said first buffer comprises first one-way valve 612 arranged side by side, first segment head piece 613 and first relief valve 614; Said first lower end mouth 221 directly is communicated with second hydraulic power 621 by runner; Second lower end mouth 222 is communicated with second hydraulic power 621 through second buffer again, and said second buffer comprises second one-way valve 622 arranged side by side, second restriction 623 and second relief valve 624.The wherein effect of one-way valve: forward supplies pressure oil, oppositely forms buffer cavity by oil return; Restriction effect: buffering throttling; The restriction of reasonable orifice size is set, makes piston rod seating velocity when the last braking of buffer stage little, stable, cushioning effect receives influence of temperature change little.The relief valve effect: limit the buffering surge pressure through overflow, avoid in buffering course reducing valve motion speed too early and prolong buffer time, when high engine speeds turned round, long buffer time can influence normal distribution function; Relief valve can preferentially adopt the adjustable relief valve of oil pressure relief, and the buffering surge pressure can be regulated and control according to the difference of loading condition.Valve buffer time can be less than 0.7 millisecond when high engine speeds, so relief valve should have very high speed of response in design.
On the end face of said first piston bar first shaft shoulder 412 near first piston bar second neck 413 at least one first segment chute 4121 is arranged, said first segment chute 4121 is the variable throttling area, diminishes gradually along the second direction area; On the end face of said second piston rod, first shaft shoulder 422 near second piston rod, second neck 423 at least one second throttling groove 4221 is arranged, said second throttling groove 4221 is the variable throttling area, diminishes gradually along the first direction area.Throttling groove variable throttling area design makes piston rod obtain buffering course stably.
Shown in Figure 1 is the little lift original state of actuator valve; The said driving spring 512 of going up has just possessed certain amount of spring compression when original state; Spring control cylinder block upper surface 5131 contacts with cavity first confined planes 251; The i.e. second hydraulic power voltage supply of power piston 300 cavity of resorption voltage supply acts on the reaction force of hydraulic action much larger than last driving spring 512 along second direction on power piston 300 second surfaces 320 along first direction, and the first surface 310 of power piston 300 contacts with first end 231; The first piston bar 410 and second piston rod 420 are in original state, valve-closing at this moment.
In conjunction with Fig. 1, shown in Figure 2; The little lift working procedure of actuator valve is following: when hydraulic control circuit switches to system high pressure (PH) and system low-voltage (PL) respectively with first hydraulic power 611 and second hydraulic power 621; The epicoele of power piston 300 and cavity of resorption also receive system high pressure (PH) and system low-voltage (PL) respectively; Power piston 300 and piston rod 410 and 420 spring make a concerted effort and the acting in conjunction of hydraulic coupling under stretch out certain stroke (approximate the length L 1 in first effective oil pressure chamber of actuation-cylinder 230, accurate stroke is influenced by amount of spring compression and system pressure within the specific limits) fast, driving valve 700 is opened; Last driving spring 512 decrements discharge; Following driving spring 522 decrements increase, and second piston rod, first shaft shoulder 422 is closed the cavity of resorption oil circuit simultaneously, and valve stays open state.When hydraulic control circuit switches back first hydraulic power 611 and second hydraulic power 621 respectively when being system low-voltage (PL) and system high pressure (PH); The epicoele of power piston 300 and cavity of resorption also receive system low-voltage (PL) and system high pressure (PH) respectively, and power piston 300 and piston rod 410 and 420 are withdrawn like the original state of Fig. 1 at spring with joint efforts and under the acting in conjunction of hydraulic coupling.The motion of whole actuator mainly is by disymmetry pressure spring (driving spring 512 and 522 up and down) telescopic oscillating power (conversion of gesture kinetic energy) to be provided, and oil hydraulic circuit replenishes the energy loss in the spring reciprocating vibration process, and control valve switch state.
The present invention makes piston rod different with the system fuel feeding logic of stroke end of a period during the stage in the back and forth movement starting stage to the design of piston rod; When the starting stage that piston rod moves along first and second directions, system oil return is directly got back to fuel tank through first upper end-hole 211 and first lower end mouth 221 respectively; And when the stroke that moves along first and second directions is ended the stage; System oil return must be respectively through arriving the damping device of setting behind second upper end-hole 212 and second lower end mouth, 222 buffer cavitys; Just can get back to fuel tank at last, realize two ends stroke end of a period buffering with the damping device cooperating like this.
Be illustrated in figure 3 as actuator valve high-lift original state; Spring pilot pressure (PS) is got a high value; Hydraulic coupling foot drives along second direction in spring being controlled cylinder block 513, contacts with cavity second confined planes 252 until spring control cylinder block lower surface 5132, has increased the pre compressed magnitude (state in Fig. 1) of last driving spring 512 greatly; The equinoctial point of making a concerted effort of last driving spring 512 and following driving spring 522 is moved along second direction, to increase the lift of valve.First hydraulic power 611 and second hydraulic power 621 (so the epicoele of power piston 300 and cavity of resorption also) be connected system low pressure (PL) and high pressure (PH) respectively; Act on hydraulic action on power piston 300 second surfaces 320 greater than the reaction of driving spring 512 and 522 make a concerted effort (this moment is along second direction) along first direction; The first surface 310 of power piston 300 contacts with first end 231; This moment, piston and piston rod 300,410 and 420 were in original state, valve-closing.
In conjunction with Fig. 3, shown in Figure 4; Actuator valve high-lift working procedure is following: when hydraulic control circuit switches to system high pressure (PH) and system low-voltage (PL) respectively with first and second hydraulic power 611 and 621 (shown in Figure 4); The epicoele of power piston 300 and cavity of resorption also receive system high pressure (PH) and system low-voltage (PL) respectively, and power piston 300 and piston rod 410 and 420 are made a concerted effort and the acting in conjunction lower edge second direction of hydraulic coupling is stretched out fast at spring; In this process, the hydraulic oil of the epicoele of power piston 300 replenishes through one-way valve 612.After the first surface 310 of power piston goes out first edge 241; Fluid bypass 240 is the short circuit first fluid space and second fluid space effectively; The epicoele of power piston 300 and cavity of resorption are basically under same pressure and lose corresponding hydraulic coupling and save unnecessary hydraulic pressure energy consumption, and power piston 300 and piston rod 410 and 420 continue to move along second direction under the effect that inertial force and spring are made a concerted effort.After power piston 300 and piston rod 410 and 420 were gone the halfway of about lift; The spring direction of making a concerted effort to begin to change, resisted motion, and at the volley kinetic energy is changed into and puts aside potential energy; But power piston 300 and piston rod 410 and 420 also move downward under the ordering about of inertial force, and progressively slow down.After the second surface 320 of power piston 300 is crossed second edge 242; Fluid bypass 240 is closed; The epicoele of power piston 300 and cavity of resorption be recovery system high pressure (PH) and system low-voltage (PL) effect respectively also; Second piston rod, first shaft shoulder 422 separates first lower end mouth 221 and second lower end mouth 222, and as buffer cavity (second throttling groove 4221 on second piston rod, first shaft shoulder 422 is as the part of buffer structure), power piston 300 and piston rod 410 and 420 are behind buffer deceleration with second lower end mouth 222; The second surface 320 of power piston 300 overlaps with the second end 232 of housing 200; Movement travel ends, and drives opening of valve 700 to high-lift, and last driving spring 512 decrements discharge; Following driving spring 522 decrements increase, and the hydraulic coupling foot on the power piston 300 keeps the open mode of valve 700 in the with joint efforts reverse of opposing driving spring.In above-mentioned buffering course, one-way valve 622 is in closed condition always under the effect of backpressure; Second throttling groove 4221 release portion hydraulic oil when buffering initial is back to the actuation-cylinder epicoele and causes bounce-back to prevent excessively buffering; Second restriction 623 is in circulation status always, attempts to be created in the compensator or trimmer pressure in the buffer cavity by its choked flow character, and this compensator or trimmer pressure acts on the cushion effect that forms power piston second surface 320 and reduces power piston and the speed of the movement parts that links to each other; Because the variation of engine operating condition, above-mentioned buffering element also have narrow limitation together, possibly cause the compensator or trimmer pressure transient state too high and draw backlash or buffer time long, second relief valve 624 can be opened fast to transient state and reduces the buffering surge pressure for this reason.
When hydraulic control circuit switches back first hydraulic power 611 and second hydraulic power 621 respectively when being system low-voltage (PL) and system high pressure (PH); The epicoele of power piston 300 and cavity of resorption also receive system low-voltage (PL) and system high pressure (PH) respectively; Power piston 300 and piston rod 410 and 420 make a concerted effort to reach the original state of the acting in conjunction lower edge first direction withdrawal of hydraulic coupling like Fig. 3 at spring, and the logical course of its movement process and valve opening procedure are similar and opposite.
The little lift operating mode of valve is mainly used in engine start and the little load operation of low speed, and valve high-lift operating mode is mainly used in the middle and high fast high load working condition of motor.
In Fig. 4, when second piston rod 420 moves to when the second direction stroke is ended the stage, second piston rod, first shaft shoulder 422 separates first lower end mouth 221 and second lower end mouth 222 respectively, with first lower end mouth 221 as buffer cavity; Second throttling groove 4221 on second piston rod, first shaft shoulder 422 is as the part of buffer structure.
Shown in Figure 5 is the variant of actuator structure embodiment illustrated in fig. 1; Be with a big difference of actuator structure shown in Figure 1: all direct oil sump tank 615 of first upper end-hole 211 and first lower end mouth 221; This structure in some design proposal is simpler, and does not influence the original intention (i.e. the oil return function of first upper end-hole 211 and first lower end mouth 221) of this two-port design function; Damping device is made up of the one-way valve and the relief valve of parallel connection.
The big difference of another of Fig. 5 and actuator structure shown in Figure 1 is: restriction also designs one or more oil grooves or the openning on the valve port of relief valve or one-way valve in Fig. 5, and oil groove is also can be through-flow on a small quantity at relief valve or closed check valve.In Fig. 5, first segment head piece 6121 is combined on the valve port of first one-way valve 612 ', and second restriction 6241 is combined on the valve port of second relief valve 624 '.
Embodiment among relative Fig. 1; Another kind of embodiment of the present invention can make the diameter of the diameter of the first piston bar second shoulder axle 414 less than the first piston bar first shoulder axle 412; So that moving along second direction at valve 700 has an extra driving force when being descending, to help to overcome extra resistance to motion (similar engine exhaust port is run into when opening); Accordingly; First control hole 271 also can be divided into respectively takes on two-part that the 412 and second shoulder axle 414 matches (demonstration among Fig. 1) with first piston bar first, but their internal diameter is complementary with first piston bar first respectively with takeing on an external diameter slide relative of the 412 and second shoulder axle 414.
In a lot of diagrams with in describing, flowing medium is assumed to oil or hydraulic pressure or liquid form, and under most of situation, same notion can suitably be applied to air pressure or water quality oil hydraulic actuator and system after the design in proportion.Equally, mean at the term " fluid " that this adopted and comprise liquids and gases.
Although in foregoing description and Fig. 1-5; First and second piston rod is symmetry basically; Under them or also symmetry basically of corresponding first and second mobile mechanism; But the present invention also comprises actuator, piston rod that one of them is instructed for foregoing description and Fig. 1-5 and under or corresponding mobile mechanism, and another piston rod and under or corresponding mobile mechanism can adopt the piston rod in the prior art and the mechanism design (with reference to Chinese patent ZL200680021728.6) that flows.
The above is merely embodiments of the invention; Be not so limit claim of the present invention; Every equivalent structure or equivalent flow process conversion that utilizes specification of the present invention and accompanying drawing content to be done; Or directly or indirectly be used in other relevant technical fields, all in like manner be included in the scope of patent protection of the present invention.
Claims (12)
1. actuator comprises:
Housing has upper end-hole and lower end mouth;
Actuation-cylinder in said housing, first direction longitudinally and second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is connected with said first piston bar, along the said power piston of second direction bias voltage; And have at least two original states, the initial bias voltage power of at least two different sizes is provided to said power piston;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said first piston bar, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part.
2. actuator according to claim 1; It is characterized in that said first spring system comprises first driving spring, spring seat, spring control cylinder block and plunger; Said first driving spring is placed oneself in the midst of between said spring seat and the said spring control cylinder block; Said spring seat is connected with said first piston bar, in the said spring control cylinder block oil pocket is arranged, and said plunger has a runner; Said housing comprises a cavity and its enable port; Said first spring system is installed in the said cavity; Runner is communicated with said oil pocket and said its enable port in the said plunger; Said spring control cylinder block can vertically move in said cavity with respect to said housing, with the decrement along said first driving spring of vertical change.
3. actuator comprises:
Housing has upper end-hole and lower end mouth, and said upper end-hole also comprises first upper end-hole and second upper end-hole;
Actuation-cylinder in said housing, first direction longitudinally and second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is along the said power piston of second direction bias voltage;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said second piston rod, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said first piston bar to be comprising first piston bar first neck, first piston bar first shaft shoulder, first piston bar second neck and first piston bar second shaft shoulder near the order of said power piston, its each all have outside dimensions;
Said first-class actuation mechanism comprises first control hole with Inner Dimension;
The Inner Dimension of said first control hole is a bit larger tham the outside dimensions of said first piston bar first shaft shoulder and said first piston bar second shaft shoulder; And significantly greater than the outside dimensions of said first piston bar first neck and said first piston bar second neck; And when said fluid bypass is opened basically; Said first piston bar first shaft shoulder and said first control hole vertically overlap, and said first fluid space and said upper end-hole are cut off;
When the first surface of said power piston to the approaching terminal stage of the first end of said actuation-cylinder; Said first piston bar first shaft shoulder is the part of said first control hole of overlapping between said first upper end-hole and said second upper end-hole vertically, to cut off first upper end-hole and second upper end-hole.
4. actuator according to claim 3; It is characterized in that; The outside dimensions of the said first piston bar second shoulder axle is less than the outside dimensions of the said first piston bar first shoulder axle; Accordingly; Said first control hole comprises respectively a first portion and a second portion that matches with said first piston bar first shoulder axle and the said first piston bar second shoulder axle, but the Inner Dimension of said first portion be complementary with the said first piston bar first shoulder axle slide relative ground, but the outside dimensions slide relative of the Inner Dimension of said second portion and said first piston bar second shoulder spool be complementary.
5. actuator according to claim 3 is characterized in that, on the end face of said first piston bar first shaft shoulder near said first piston bar second neck at least one first segment chute is arranged.
6. actuator according to claim 3; It is characterized in that; When said actuator also comprises first buffer with the first end of advancing at said power piston near said actuation-cylinder; The speed that suppresses said power piston, said actuator also comprise first hydraulic power that is communicated in said upper end-hole, and said first buffer is positioned on the runner that is communicated with said second upper end-hole and said first hydraulic power.
7. actuator according to claim 6 is characterized in that, said first buffer comprises first one-way valve, first segment head piece and first relief valve of parallel connection.
8. actuator according to claim 7 is characterized in that, said first relief valve is adjustable relief valve.
9. actuator comprises:
Housing has upper end-hole and lower end mouth, and said lower end mouth also comprises first lower end mouth and second lower end mouth;
Actuation-cylinder in said housing, first direction longitudinally and second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
The first piston bar is connected to the first surface of said power piston;
Second piston rod is connected to the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First spring system is along the said power piston of second direction bias voltage;
Second spring system is along the said power piston of first direction bias voltage;
First-class actuation mechanism cooperates with said first piston bar, controls fluid connection between said first fluid space and the said upper end-hole;
The second mobile mechanism cooperates with said second piston rod, controls fluid connection between said second fluid space and the said lower end mouth;
Wherein: when said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said second piston rod to be comprising second piston rod, first neck, second piston rod, first shaft shoulder, second piston rod, second neck and second piston rod, second shaft shoulder near the order of said power piston, its each all have outside dimensions;
The said second mobile mechanism comprises second control hole with Inner Dimension;
The Inner Dimension of said second control hole is a bit larger tham the outside dimensions of said second piston rod, first shaft shoulder and said second piston rod, second shaft shoulder; And significantly greater than the outside dimensions of said second piston rod, first neck and said second piston rod, second neck; And when said fluid bypass is opened basically; Said second piston rod, first shaft shoulder and said first control hole vertically overlap, and said second fluid space and said lower end mouth are cut off;
When the second surface of said power piston to the approaching terminal stage of the second end of said actuation-cylinder; Said second piston rod, first shaft shoulder is the part of said second control hole of overlapping between first lower end mouth and second lower end mouth vertically, to cut off said first lower end mouth and said second lower end mouth.
10. actuator according to claim 9 is characterized in that, on the end face of said second piston rod, first shaft shoulder near second piston rod, second neck at least one second throttling groove is arranged.
11. actuator according to claim 9; It is characterized in that; When said actuator also comprises second buffer with the second end of advancing at said power piston near said actuation-cylinder; The speed that suppresses said power piston, said actuator also comprise second hydraulic power that is communicated in said lower end mouth, and said second buffer is positioned on the runner that is communicated with said second lower end mouth and said second hydraulic power.
12. actuator according to claim 11 is characterized in that, said second buffer comprises second one-way valve, second restriction and second relief valve of parallel connection.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100951845A CN102606251B (en) | 2012-03-31 | 2012-03-31 | Variable valve actuator |
| US13/850,372 US8978604B2 (en) | 2012-03-31 | 2013-03-26 | Variable valve actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100951845A CN102606251B (en) | 2012-03-31 | 2012-03-31 | Variable valve actuator |
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| CN102606251A true CN102606251A (en) | 2012-07-25 |
| CN102606251B CN102606251B (en) | 2013-11-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2012100951845A Expired - Fee Related CN102606251B (en) | 2012-03-31 | 2012-03-31 | Variable valve actuator |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103104307A (en) * | 2013-01-24 | 2013-05-15 | 江苏公大动力技术有限公司 | Variable throttling device |
| CN103322186A (en) * | 2013-06-26 | 2013-09-25 | 临海市优力达机械有限公司 | Low-impact speed change control valve for loader |
| CN103953411A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Two-stage boosting air valve type air exhaust mechanism |
| CN103953410A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Variable-driving-pressure pressure boosting type exhaust mechanism |
| CN107842642A (en) * | 2017-12-12 | 2018-03-27 | 大连亨利测控仪表工程有限公司 | High-effect cut-out type single-acting pneumatic actuator |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007016519A2 (en) * | 2005-08-01 | 2007-02-08 | Lgd Technology, Llc | Variable valve actuator |
| CN101198772A (en) * | 2005-06-16 | 2008-06-11 | Lgd技术股份有限公司 | Variable valve actuator |
| CN202628212U (en) * | 2012-03-31 | 2012-12-26 | 江苏公大动力技术有限公司 | Actuator for variable air valve |
-
2012
- 2012-03-31 CN CN2012100951845A patent/CN102606251B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101198772A (en) * | 2005-06-16 | 2008-06-11 | Lgd技术股份有限公司 | Variable valve actuator |
| WO2007016519A2 (en) * | 2005-08-01 | 2007-02-08 | Lgd Technology, Llc | Variable valve actuator |
| CN202628212U (en) * | 2012-03-31 | 2012-12-26 | 江苏公大动力技术有限公司 | Actuator for variable air valve |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103104307A (en) * | 2013-01-24 | 2013-05-15 | 江苏公大动力技术有限公司 | Variable throttling device |
| CN103104307B (en) * | 2013-01-24 | 2016-01-20 | 宁波华液机器制造有限公司 | Variable throttling device thereof |
| CN103322186A (en) * | 2013-06-26 | 2013-09-25 | 临海市优力达机械有限公司 | Low-impact speed change control valve for loader |
| CN103953411A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Two-stage boosting air valve type air exhaust mechanism |
| CN103953410A (en) * | 2014-03-21 | 2014-07-30 | 哈尔滨工程大学 | Variable-driving-pressure pressure boosting type exhaust mechanism |
| CN107842642A (en) * | 2017-12-12 | 2018-03-27 | 大连亨利测控仪表工程有限公司 | High-effect cut-out type single-acting pneumatic actuator |
| CN107842642B (en) * | 2017-12-12 | 2024-04-02 | 大连亨利测控仪表工程有限公司 | High-efficiency cut-off type single-action pneumatic actuating mechanism |
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|---|---|
| CN102606251B (en) | 2013-11-27 |
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Effective date of registration: 20150515 Address after: 315000 Zhejiang city of Ningbo Province Wang town Yinzhou District week Jiacun Patentee after: Ningbo Hoyea Machine Manufacturing Co., Ltd. Address before: Four road 215513 Jiangsu Branch Park City in Suzhou Province, Changshu economic and Technological Development Zone No. 11 Room 303 Patentee before: Jiangsu Gongda Power Technologies Co., Ltd. |
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