CN1690371A - Actuator having driving cam and valve lift controller employing the same - Google Patents
Actuator having driving cam and valve lift controller employing the same Download PDFInfo
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- CN1690371A CN1690371A CN 200410032966 CN200410032966A CN1690371A CN 1690371 A CN1690371 A CN 1690371A CN 200410032966 CN200410032966 CN 200410032966 CN 200410032966 A CN200410032966 A CN 200410032966A CN 1690371 A CN1690371 A CN 1690371A
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Abstract
The invention discloses an actuator, which controls the liftrange of vehicle engine air admission valve (35). One end of control shaft (30) connects a transmission means, while another end connects the valve liftrange controller. The control shaft is designed as a spindle, which is vertical to the generator. Furthermore, said transmission means comprises an inner drive cam (52). So, whatever the length of generator (20) is, the size of actuator (10) on the longitudinal direction of control shaft (30) is very small. And the control shaft (30) reciprocating moves according to the contour profile of drive cam (52) when the generator (20) runs. By limiting the contour of cam, especially the contour in the section corresponding to the idling behavior of engine, the liftrange of air admission valve (35) can be controlled accurately.
Description
Technical field
The present invention relates to a kind of actuator, its axial position according to a Control Shaft is operated a controlled object, simultaneously the rotation of a motor is changed into the to-and-fro motion of Control Shaft, the invention still further relates to the valve lift control system that adopts this actuator.
In vehicular engine, used an actuator, be used for one controlled object being operated according to the axial position of a Control Shaft.
Background technique
Disclosed in according to No. 6425357 U. S. Patent (JP-A-2001-263015), as to be used for internal-combustion engine variable valve actuator for air, a middle driving mechanism is movably supported on its axis, and this axis is independent of the axis of air valve cam.Middle driving mechanism comprises the parts that a Control Shaft, parts relevant with the air valve cam and some and suction valve are correlated with.Driving mechanism is to pass to suction valve for the driving force with the air valve cam in the middle of being provided with.The to-and-fro motion of Control Shaft is converted into the rotational motion of air valve cam associated components and the rotational motion of suction valve associated components.Thereby, can come the relative lift between one control air valve cam associated components and the suction valve associated components poor based on the axial position of Control Shaft.Herein, controlled object also can be outlet valve but not suction valve.
But, be to be undertaken by the oil pressure of regulating in the pressure chamber to the control of the axial position of Control Shaft.It is distolateral that the pressure chamber is set at one of Control Shaft, is used to make the Control Shaft to-and-fro motion.In this structure, be provided with a piston and a housing that is used to form the pressure chamber that is used to bear the oil pressure that comes from the pressure chamber, so just can the control piston front side and dorsal part between pressure difference.Thereby the controllability of position and responsiveness are very poor.
In this regard, can adopt an electric actuator to replace hydraulic actuator.But according to the arrangement relation of motor and Control Shaft, on the axial direction of Control Shaft, the length of motor-driven cylinder may be very long.
Summary of the invention
Consider above-mentioned problem, an object of the present invention is to propose a kind of actuator, its small-sized on the Control Shaft axial direction, the present invention also provides a kind of valve lift controller that adopts this actuator.
The axle that is used for the motor of rotating drive cam is arranged perpendicular to the Control Shaft of this actuator.Thereby the length of motor can directly not influence the length of actuator on Control Shaft is axial.Like this, can be with the shorten length of actuator.
Be provided with a spur gear coaxially with driving cam, be used to rotate this driving cam.On two side planes of spur gear, be shaped on two protruding keys.Corresponding with the position of projection that is used for spur gear is carried out locking, on the both sides of spur gear, be provided with retainer dividually.Thereby, can prevent to interfere between retainer and the projection.
One transmission device and the Control Shaft that will comprise described driving cam are joined together, and are used for the rotation of interior driving cam is changed into the to-and-fro motion of Control Shaft.Transmission device is configured to like this: the axis normal of driving cam makes transmission device and Control Shaft overlapped in the axis of Control Shaft simultaneously in making.Thereby the length of anastomosis part on Control Shaft is axial can be shortened between Control Shaft and the transmission device.
Utilize a rotary angle transmitter that adopts Hall (Hall) element that the corner of driving cam is detected.This detection belongs to non-contact detection, thereby can improve the reliability of rotary angle transmitter, and can prolong the operating life of rotary angle transmitter.
One magnetic clutch is set in actuator, when this magnetic clutch dead electricity, can stops motor to rotate, thus the fixing position of Control Shaft.Thereby, be longer than the situation of its run duration for the total stop time of controlled object in the course of the work, if on actuator, used this magnetic clutch, then just can reduce the energy consumption of motor.
When motor during at idle running, the angle of driving cam is limited in the angular interval, this angular interval be in its rotate interval range one end near.In this regard, the rotation of driving cam is equal to the lift of suction valve.
When driving cam turns near its slewing area terminal, the variance ratio of suction valve lift (lift change rate) is restricted to less than a suction valve lift variation rate score, and back one variance ratio numerical value is meant when driving cam and turns to variance ratio when not belonging between slewing area end peripheral region.Therefore, the variance ratio of driving cam lift reduces with respect to the driving cam rotation angle.Therefore, the displacement amount of Control Shaft on its reciprocating direction is also with respect to the rotation angle of driving cam and reduce.Detect the displacement (being the lift of suction valve) that obtains Control Shaft by rotation angle herein, to driving cam.
Thereby, in the time of can improving engine idle to the testing precision of Control Shaft displacement.Thereby can implement accurate control to the axial position of Control Shaft, and then can accurately control the lift of suction valve.In this regard, controlled object can be outlet valve but not suction valve.
When Control Shaft when for example controlling for the lift of the controlled object of suction valve or outlet valve, it can be subjected to coming from the reaction force of controlled object.
Description of drawings
From the detailed description of hereinafter doing with reference to accompanying drawing, can more clearly understand other purpose, feature and advantage of the present invention, in the accompanying drawings:
Fig. 1 is the perspective view of a partly cut-away, has represented the actuator according to first embodiment of the invention;
Perspective representation among Fig. 2 Control Shaft and according to the joint area between the transmission device of first mode of execution;
Fig. 3 is the side view of transmission device being done along arrow III direction among Fig. 2;
Among Fig. 4 the perspective representation of partly cut-away the projection on cam wheel;
Waveform figure line among Fig. 5 has been represented the load that driving cam applied by the lift controller;
Figure line among Fig. 6 has been represented cam angle, driving cam lift and has been affacted relation between the moment on the driving cam;
Fig. 7 is a schematic side view, has expressed one and has affacted the direction of the load on the driving cam and the arm of force length of driving cam;
Figure line among Fig. 8 has been represented the cam angle of driving cam and the relation between the cam lift; And
Among Fig. 9 the perspective representation of partly cut-away according to the actuator of second embodiment of the invention.
Embodiment
[first mode of execution]
As shown in Figure 1, for example, actuator 10 is used to drive a valve lift controller 38 that is used on the internal-combustion engine.In this, valve lift controller 38 is controlled the relative lift difference between a suction valve 35 and the air valve cam 36 according to the axial position of a Control Shaft 30.Air valve cam 36 is being controlled the switching of suction valve 35.
One end of Control Shaft 30 engages with the support frame 41 of transmission device 40, and the other end then engages with valve lift controller 38.The axis normal of Control Shaft 30 is in the axis of motor 20 axles 24.
As shown in Figures 2 and 3, be shaped on a shaft coupling portion 32 on an end of Control Shaft 30, this a shaft coupling portion and a joint 42 are assembled together.Shaft coupling portion 32 is joined to the joint 42 of support frame 41, just shaft coupling portion 32 can be assembled mutually, splices with joint 42.Utilize a clip 46 that the joint area between shaft coupling portion 32 and the joint 42 is linked up, thereby they are secured to together.
Return referring to Fig. 1, the two ends of camshaft 50 are provided with cam wheel 54,56 again.Cam wheel 54 is meshed with motor gear 28.Motor gear 28 and cam wheel 54 all are spur gears, and the two is used as reduction gear to (braking section 28,54).
As shown in Figure 4, on an end face of cam wheel 54, be shaped on a protruding key (giving prominence to) 54a.Be provided with a bar axle 70 on the housing of motor 20, it is used as retainer.When protruding key 54a was withstood by bar axle (retainer) 70, motor 20 stopped operating.On an axially opposite side, be shaped on another protruding key (giving prominence to) 54b on second end face of cam wheel 54 with protruding key 54a with respect to cam wheel 54.The housing of motor 20 is provided with another bar axle (retainer) 72, itself and the bar axle 70 the same retainers that also are used as.When protruding key 54b and bar axle 72 offseted, motor 20 stopped operating.Herein, two bar axles the 70, the 72nd, branch is arranged, thereby can prevent to interfere between the two.
Two protruding key 54a, 54b carry out locking by two bar axles 70,72 respectively, are limited in about 300 ° scope thereby make between the rotational area of driving cam 52.When engine idling operation, first end between driving cam 52 rotational area corresponds essentially to the lift of suction valve 35.
Refer again to Fig. 1, a rotary angle transmitter 60 has a measuring gear 62 that is meshed with cam wheel 56.On measuring gear 62, be provided with an inspected object (not shown) coaxially.This rotary angle transmitter 60 utilizes a contactless Hall element to detect the rotation angle of inspected object, can detect the rotation angle of camshaft 50 from you.Herein, rotary angle transmitter 60 does not contact any object, thereby can improve the reliability of this rotary angle transmitter, and can prolong the working life of this sensor.By the velocity ratio between cam wheel 56 and the measuring gear 62 is set, the angle range of inspected object can be limited in the 90 degree scopes.Thereby the angle range of inspected object is in the interval that Hall element can detect rotary member.
Signals such as the signal of ECU80 input rotary angle transmitter 60, accelerometer position signal, and, come drive motor 20 with this to EDU82 output control signal.
To the working procedure of this actuator be described below.
When motor 20 rotated, the moment of torsion of motor 20 passed to camshaft 50 and driving cam 52 (see figure 3)s by motor gear 28 and cam wheel 54.
As shown in Figure 3, when driving cam 52 rotates, support frame 41 Control Shaft 30 axially on to-and-fro motion linearly.The roller 44 that supported framework 41 is supporting also slides on the surface of driving cam 52 when rolling, thereby support frame 41 is moved reposefully.Valve lift controller 38 is controlled with respect to the relative lift difference of air valve cam 36 suction valve 35 according to the axial position of Control Shaft 30, and the to-and-fro motion of Control Shaft is then corresponding to the profile molded lines of driving cam 52 camming surfaces (outer circumferential face) 53.
When 30 pairs of suction valves 35 of Control Shaft were controlled with respect to the relative lift difference of air valve cam 36, Control Shaft 30 was subjected to coming from the reaction force of suction valve 35.This reaction force is represented as load 200 in Fig. 5.At driving cam 52 when the end (first end) of its slewing area turns to the other end (second end), reaction force (load) variation that changes, and after about 0.6 second, driving cam stops operating in second tail end.Each peak value of load 200 is corresponding to the rising each time of the suction valve 35 of each cylinder in four cylinders.Along with driving cam 52 turns to second end from first end between its rotational area, the load that is affacted on the Control Shaft 30 by valve lift controller 38 increases gradually.After driving cam 52 forwards second end to, because driving cam 52 no longer is subjected to coming from the reaction force of suction valve 35 when rotating, so the load meeting reduces.
When driving cam 52 is parked on second end between its rotational area, the load when the suffered load of driving cam 52 is in first end between its rotational area greater than the angle when driving cam 52.
Shown in the straight line among Fig. 6 210, the profile molded lines of driving cam 52 is restricted to the lift that makes cam to be changed linearly with the corner of driving cam 52.As shown in Figure 7, the arm of force length δ of driving cam 52 is defined as the normal 102 of driving cam 52 and the distance between camshaft 50 centers.For the profile molded lines of Fig. 6 cathetus 210 representatives, when first end of driving cam 52 between its rotational area turned to second end, its arm of force length δ kept constant basically.Shown in the straight line among Fig. 6 212, when first end of driving cam 52 between its rotational area turned to second end, the moment that is imposed on driving cam 52 by valve lift controller 38 increased linearly.
On the other hand, if the profile molded lines of driving cam 52 is another curves shown in the curve 214 among Fig. 6, and this curve 214 is the parabola of upside projection, then when first end of driving cam 52 between its rotational area turns to second end, the variance ratio of driving cam 52 lifts (lift change rate) just constantly reduces after moment increases subsequently.Refer again to Fig. 7, when first end of driving cam 52 between rotational area turned to second end, normal 102 approached to the axis of driving cam 52, thereby the arm of force length of driving cam 52 can shorten.
The action direction of load F is: with respect to the tangent line 100 at its point of action place on cam face 53, apply effect along the normal 102 at this some place.At this on the one hand, when driving cam 52 from first end between its rotational area when second end rotates, load F can increase gradually.That is to say that when the arm of force length δ of driving cam 52 reduced, the load F that affacts driving cam 52 was but increasing.
Can calculate valve lift controller 38 like this to moment that driving cam 52 applies: it is to affact load F on the driving cam 52 and the product (F δ) of driving cam 52 arm of force length δ.
In this, when arm of force length δ increased, load F was but reducing, thereby, in between the whole rotational area of driving cam 52, the product of load F and arm of force length δ (promptly affacting moment on the Control Shaft 30 by suction valve 35) can keep constant basically.
Thereby, can reduce to affact the maximum moment on the driving cam 52.Herein, motor 20 required moments are based on driving cam 52 and made by the maximum moment of valve lift controller 38 effect.Therefore, so just can reduce motor 20 desired moments of torsion.So, the size that can dwindle motor.
The rotation angle of driving cam 52 is equal to the lift of suction valve 35.When engine idling operation, the angle of driving cam 52 is in the scope near first end between its rotational area.
Shown in the figure line among Fig. 8 216, in near between rotational area first end the scope, the variance ratio of cam lift is restricted to very little value, and in an interval subsequently, it is big that the cam lift variance ratio just becomes, and this interval is to be the development of starting point and second end between rotational area near extremity of an interval first end.In the case, near first end between rotational area, driving cam 52 lifts are very little with respect to the variance ratio of its rotation angle.Therefore, when driving cam 52 rotated near first end, the displacement amount of Control Shaft 30 on reciprocating direction was very little.Thereby suction valve 35 lifts are to reduce value with respect to the variance ratio of driving cam 52 rotation angles.
The profile molded lines of driving cam 52 can be the curve 218 shown in Fig. 8, and among the figure, curve 218 is the parabola of upside projection, and than near interval interior lift variation rate non-first end, the lift variation rate of the first end vicinity is less between rotational area.In the case, when motor is in idling mode, can accurately control the lift of suction valve 35.In addition, can also reduce the maximum moment that affacts on the driving cam 52.
[second mode of execution]
As shown in Figure 9, with respect to axle 24 and a side opposite with motor gear 28, motor 80 is provided with a magnetic clutch 90.This magnetic clutch 90 comprises a rolling disc 91, a stator 92, a coil 94, an armature 96 and a slice spring 97.Rolling disc 91 quilt covers are pressed onto on the axle 24, thereby can rotate with axle 24.When not switching in coil 94, armature 96 is pressed on the rolling disc 91 by sheet spring 97.Sheet spring 97 is partly being locked by stator 92.When armature 96 was pressed onto on the rolling disc 91 by sheet spring 97, the rotation of axle 24 just had been subjected to the restriction of rubbing action between armature 96 and the rolling disc 91.That is to say that when not to coil 94 energisings, the rotation of motor 80 is stopped.When to coil 94 energisings, electromagnetic force overcomes the roof pressure power of sheet spring 97 and armature 96 is pulled to stator 91, thereby armature 96 and rolling disc 91 are separated.Like this, axle 24 is just freed from its constrained state.
When actuator 10 was used to drive a valve lift controller, it is long that the 30 out-of-work times of Control Shaft will be carried out the reciprocating time by it.That is to say that the time that the lift of suction valve 35 remains unchanged will be longer than the time that its lift changes.When coil 94 dead electricity of magnetic clutch 90, the rotation of motor 80 is stopped, thereby has just stopped the to-and-fro motion of Control Shaft 30, and then has just fixed the lift of suction valve 35.Under the situation that suction valve 35 lifts are fixed, need not to power.Thereby, can reduce and be used for power supply that the lift of suction valve 35 is controlled.
Can be and use an overrunning clutch and a friction disk in the clutch mechanism of magnetic clutch.In the case, when when magnetic clutch is switched on, overrunning clutch can rotate on both direction.On the other hand, when the magnetic clutch dead electricity, overrunning clutch can only rotate in one direction, and this direction for example is the opposite direction of suction valve lift Control Shaft reaction force.When magnetic clutch gets when electric, friction disk can rotate on two directions.On the other hand, when the magnetic clutch dead electricity, friction disk all is being connected on both direction, is used to produce a rubbing action, and the rubbing action that is produced is weaker than the driving power of motor 80.In the case, if the lift Control Shaft of suction valve is being fixed, even then clutch is being engaged, the driving power of motor 80 can guarantee that also it rotates, and has also reduced the power consumption of motor 80 simultaneously.If used this friction disk, then can need not to use magnetic clutch and engaging this friction disk all the time.
Also can not adopt roller 44, directly support frame 41 be operated, so that realize the to-and-fro motion of Control Shaft 30 by driving cam 52.In addition, driving cam 52 also can with when sliding mutually, directly Control Shaft is being operated with Control Shaft 30.
This actuator 10 can be used in and is used for the lift of outlet valve but not the valve lift control apparatus that the lift of suction valve 35 is controlled.
The various changes and the modification that are understood that other also will covered in the protection domain of the present invention that is limited by appended claims.
Claims (8)
1, a kind of actuator devices that a controlled object is operated of being used for, this actuator comprises:
Motor (20), it has axle (24);
Control Shaft (30), it is driven by axle (24), wherein, and Control Shaft (30) to-and-fro motion on its axial direction, thus determined the operation amount of this actuator devices according to its axial position;
Driving cam (52), its rotation axis is parallel to the axis of motor (20) axle (24), wherein, the rotation axis of driving cam (52) is perpendicular to the axis of Control Shaft (30), thereby, when driving cam (52) rotates, its profile molded lines, on direction, order about Control Shaft (30) to-and-fro motion perpendicular to motor (20) axle (24) axis according to self outer circumferential face (53); And
Deceleration part (28,54), it has adopted spur gear (28,54), is used for the moment of torsion of motor (20) is passed to driving cam (52).
2, actuator devices according to claim 1 is characterized in that also comprising:
Retainer (70,72), they are with respect to the axial direction of spur gear (54) and lay respectively at its both sides;
With respect to the axial direction of spur gear (54) and be respectively formed at the projection (54a, 54b) of its both sides, each projection (54a, 54b) is being supported by the retainer of correspondence (70,72) respectively, be used to limit between the rotational area of spur gear (54),
Wherein:
Spur gear (54) rotates coaxially with the rotating shaft (50) of driving cam (52); And
The rotation angle of driving cam (52) is limited between the end and the other end between spur gear (54) rotational area between spur gear (54) rotational area.
3, a kind of actuator devices that a controlled object is operated of being used for, this actuator comprises:
Motor (20), it has axle (24);
Control Shaft (30), it is driven by axle (24), wherein, and Control Shaft (30) to-and-fro motion on its axial direction, thus determined the operation amount of this actuator devices according to its axial position;
Driving cam (52), its rotation axis is parallel to the axis of motor (20) axle (24), wherein, the rotation axis of driving cam (52) is perpendicular to the axis of Control Shaft (30), thereby, when driving cam (52) rotates, its profile molded lines, on direction, order about Control Shaft (30) to-and-fro motion perpendicular to motor (20) axle (24) axis according to self outer circumferential face (53);
Transmission device (40), it overlaps the to each other with Control Shaft (30) and is engaging, and in the junction, the axis of driving cam (52) is arranged to the axis perpendicular to Control Shaft (30); And
Slide member (44), it is comprised in the transmission device (40) that has driving cam (52), wherein, slide member (44) is contacting mutually slidably with driving cam (52), thereby the rotational motion of driving cam (52) is converted into the to-and-fro motion of Control Shaft (30).
4, a kind of actuator devices that a controlled object is operated of being used for, this actuator comprises:
Motor (20), it has axle (24);
Control Shaft (30), it is driven by axle (24), wherein, and Control Shaft (30) to-and-fro motion on its axial direction, thus determined the operation amount of this actuator devices according to its axial position;
Driving cam (52), its rotation axis is parallel to the axis of motor (20) axle (24), wherein, the rotation axis of driving cam (52) is perpendicular to the axis of Control Shaft (30), thereby, when driving cam (52) rotates, its profile molded lines, on direction, order about Control Shaft (30) to-and-fro motion perpendicular to motor (20) axle (24) axis according to self outer circumferential face (53); And
Rotary angle transmitter (60), it adopts a Hall element to detect the rotation angle of driving cam (52) non-contactly,
Wherein, driving cam (52) to the detection range of corner less than 90 °.
5, a kind of actuator devices that a controlled object is operated of being used for, this actuator comprises:
Motor (20), it has an axle (24);
Control Shaft (30), it is driven by axle (24), wherein, and Control Shaft (30) to-and-fro motion on its axial direction, thus determined the operation amount of this actuator devices according to its axial position;
Driving cam (52), its rotation axis is parallel to the axis of motor (20) axle (24), wherein, the rotation axis of driving cam (52) is perpendicular to the axis of Control Shaft (30), thereby, when driving cam (52) rotates, its profile molded lines, on direction, order about Control Shaft (30) to-and-fro motion perpendicular to motor (20) axle (24) axis according to self outer circumferential face (53); And
Magnetic clutch (90), it is installed on the actuator (10), and wherein, when magnetic clutch (90) when being energized, it allows motor (20) to rotate, and when magnetic clutch (90) when not switching on, it does not allow motor (20) to rotate.
6, a kind of actuator devices that is arranged in the motor, is used to control valve lift, it comprises:
Actuator (10), it is used for a controlled object is operated, and this actuator (10) comprising:
Motor (20), it has an axle (24);
Control Shaft (30), it is driven by axle (24), wherein, and Control Shaft (30) to-and-fro motion on its axial direction, thus determined the operation amount of this actuator devices according to its axial position;
Driving cam (52), its rotation axis is parallel to the axis of motor (20) axle (24), wherein, the rotation axis of driving cam (52) is perpendicular to the axis of Control Shaft (30), thereby, when driving cam (52) rotates, its profile molded lines, on direction, order about Control Shaft (30) to-and-fro motion perpendicular to motor (20) axle (24) axis according to self outer circumferential face (53);
Air valve cam (36), it is used for one of opening and closing engine intake valve (35) and outlet valve; And
The lift controller, it regulates the lift of controlling suction valve (35) or outlet valve by the axial position according to Control Shaft (30) to air valve cam (36).
7, actuator devices according to claim 6 is characterized in that:
Driving cam (52) has between a rotational area, wherein, and the lift of suction valve (35) or outlet valve when the environs of one end is corresponding to engine idle between rotational area;
The cam lift of driving cam (52) has determined the amount of moving back and forth of Control Shaft (30), and wherein, when driving cam (52) rotated in slewing area, the variance ratio of cam lift changed; And
Driving cam (52) has certain profile molded lines, during near driving cam (52) turns to one end between its rotational area scope, the variance ratio of cam lift is less than a cam variance ratio, back one variance ratio numerical value be meant when driving cam turn to one with described end near extremity of an interval be variance ratio in the interval expanded of the starting point and the other end between rotational area the time.
8, actuator devices according to claim 6 is characterized in that:
Driving cam (52) has between a rotational area, wherein, and the lift of suction valve (35) or outlet valve when the environs of one end is corresponding to engine idle between rotational area;
The cam lift of driving cam (52) has determined the amount of moving back and forth of Control Shaft (30), and wherein, when driving cam (52) rotated in slewing area, the variance ratio of cam lift changed; And
Driving cam (52) has a profile molded lines, and when the end of driving cam (52) between its rotational area turned to the other end, the variance ratio of driving cam (52) lift just constantly reduced after moment increases subsequently.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200410032966XA CN100406688C (en) | 2004-04-19 | 2004-04-19 | Actuator having driving cam and valve lift controller employing the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200410032966XA CN100406688C (en) | 2004-04-19 | 2004-04-19 | Actuator having driving cam and valve lift controller employing the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1690371A true CN1690371A (en) | 2005-11-02 |
| CN100406688C CN100406688C (en) | 2008-07-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200410032966XA Expired - Fee Related CN100406688C (en) | 2004-04-19 | 2004-04-19 | Actuator having driving cam and valve lift controller employing the same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100406688C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883403A (en) * | 2014-04-18 | 2014-06-25 | 苏州工业园区职业技术学院 | Automobile engine air intake and exhaust control system based on servo control |
| CN108506157A (en) * | 2018-03-05 | 2018-09-07 | 北京航空航天大学 | Limited pivot angle rotating hydraulic actuator |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6123815A (en) * | 1984-07-11 | 1986-02-01 | Nissan Motor Co Ltd | Suction and exhaust valve lift control device for internal-combustion engine |
| JPS6123814A (en) * | 1984-07-11 | 1986-02-01 | Nissan Motor Co Ltd | Suction and exhaust valve lift control device for internal-combustion engine |
| JP3933349B2 (en) * | 1999-06-18 | 2007-06-20 | 株式会社日立製作所 | Variable valve operating device for internal combustion engine |
-
2004
- 2004-04-19 CN CNB200410032966XA patent/CN100406688C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883403A (en) * | 2014-04-18 | 2014-06-25 | 苏州工业园区职业技术学院 | Automobile engine air intake and exhaust control system based on servo control |
| CN108506157A (en) * | 2018-03-05 | 2018-09-07 | 北京航空航天大学 | Limited pivot angle rotating hydraulic actuator |
| CN108506157B (en) * | 2018-03-05 | 2019-07-23 | 北京航空航天大学 | Limited pivot angle rotating hydraulic actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100406688C (en) | 2008-07-30 |
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