CN103321706A

CN103321706A - Executing mechanism

Info

Publication number: CN103321706A
Application number: CN2013100916210A
Authority: CN
Inventors: 天野均
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2012-03-23
Filing date: 2013-03-21
Publication date: 2013-09-25
Anticipated expiration: 2033-03-21
Also published as: DE102013204878A1; JP5505744B2; CN103321706B; JP2013224646A

Abstract

The invention provides an executing mechanism of an internal combustion engine changeable air valve device. The first output spring (109) pushes a first output pin (105) towards a cam operation member (50) side arranged inside the first output pin along the axial direction of the first output pin (105). A second output spring (114) pushes a second output pin (110) towards a cam operation member (50) side arranged inside the second output pin along the axial direction of the second output pin (110). When latching rods (90, 121) are rotated to first rotation positions, the latching rods (90, 121) are jointed with the second output pin (110) and meanwhile disengaged with the first output pin (105). When the latching rods (90, 121) are rotated to second rotation positions, the latching rods (90, 121) are jointed with the first output pin (105) and meanwhile disengaged with the second output pin (110).

Description

Actuator

Technical field

The present invention relates to a kind of actuator.

Background technique

The actuator of known internal-combustion engine variable valve gear can limit the axial position of cam control spare, and this cam control spare mobile with a plurality of cams that are installed on the camshaft with being integral.For example, in the actuator of US2011/0240892A1, when a corresponding removable pin by the thrust that overcomes corresponding keep-spring to solenoid energising during towards the fixed core side shifting, some spheroids are along radially inwardly mobile.Therefore, a corresponding output pin is by the thrust of corresponding delivery spring and move towards cam control spare side.

In the actuator of US2011/0240892A1, when removable pin by applying external vibration and/or vibrations when moving axially, these spheroids are along radially inwardly mobile.Therefore, although not energising of solenoid, output pin may be towards cam control spare side shifting.

In addition, in the actuator of US2011/0240892A1, each output pin and the mutual coaxial line of corresponding removable pin.Therefore, when output pin by applying external vibration and/or vibrations when moving axially, the axial force of output pin is delivered in the removable pin by these spheroids, thereby may cause removable pin along axially moving.Therefore, identical with top situation, even when not switching on to solenoid, output pin also may be shifted to cam control spare side.

In the situation that when not shifting to cam control spare side to solenoid energising, output pin can contact the diverse location of cam control spare, this diverse location is different from the engaging groove of cam control spare when output pin, and this output pin should join in this engaging groove.In this case, thus excessive load may be applied to and causes actuator to damage in the output pin.

In addition, in the actuator of US2011/0240892A1, solenoidal size need to increase so that removable pin can overcome the thrust of keep-spring and shift to the fixed core side.Therefore the size of actuator adversely has been increased.

Summary of the invention

Owing to top shortcoming has formed the present invention.Therefore, the purpose of this invention is to provide a kind of actuator, this actuator is used in the variable valve gear and has the size of less, can prevent from damaging simultaneously actuator.

According to the present invention, provide a kind of actuator of internal-combustion engine variable valve gear.This actuator is configured to limit the axial position of cam control spare, and described cam control spare mobile with a plurality of cams that are installed on the camshaft with being integral.Described actuator comprises housing, the first removable pin, the second removable pin, latch lever, driver element, the first spring, the second spring, the first output pin, the first delivery spring, the second output pin and the second delivery spring.The first removable pin supports by housing by this way, and namely this mode is so that the first removable pin axially can move back and forth along the first removable pin.The second removable pin is arranged to be parallel to substantially the first removable pin, and supports by housing by this way, and namely this mode is so that the second removable pin axially can move back and forth along the second removable pin.The latch lever bridge joint and can rotate around the intermediate portion of latch lever between the first removable pin and the second removable pin.Described intermediate portion is between the first removable pin and the second removable pin.Driver element is configured to, axially drive the first removable pin towards an axial side along the first removable pin, thereby latch lever is rotated along a sense of rotation, and also be configured to, axially drive the second removable pin towards a described axial side along the second removable pin, thereby latch lever is rotated along described another sense of rotation, and described another sense of rotation is opposite with a described sense of rotation.The first spring promotes at least one in latch lever and the first removable pin, thereby latch lever is rotated along described another sense of rotation.The second spring promotes at least one in latch lever and the second removable pin, thereby latch lever is rotated along a described sense of rotation.The first output pin so arranges, so that the axial and imaginary plane of the first output pin is crossing, and described imaginary plane comprises a described sense of rotation and described another sense of rotation of latch lever.The first output pin supports by housing by this way, and namely this mode is so that the first output pin axially moving back and forth along the first output pin.When latch lever was positioned on the neutral position, the first output pin engaged with the intermediate portion of latch lever, wherein on described neutral position, and the mutual balance of thrust of the thrust of the first spring and the second spring.When the first output pin engages with the intermediate portion of latch lever, on the position that separates with cam control spare, can prevent that the first output pin from axially moving along the first output pin.The first delivery spring is pushed the first output pin to cam control spare along the first output pin axial and is positioned at wherein that side.The second output pin is arranged to be parallel to substantially the first output pin, and therefore the second output pin axially intersects with described imaginary plane.The second output pin supports by housing by this way, namely this mode so that the second output pin axially move back and forth along the second output pin.When latch lever was positioned on the neutral position, the second output pin engaged with the intermediate portion of latch lever.When the second output pin engages with the intermediate portion of latch lever, prevent that in the position that separates with cam control spare the second output pin from axially moving along the second output pin.The second delivery spring is pushed the second output pin to cam control spare along the second output pin axial and is positioned at wherein a side.Latch lever can rotate between the first rotational position of removing from the neutral position along a described sense of rotation and the second rotational position of removing from the neutral position along described another sense of rotation.When latch lever rotated on the first rotational position, latch lever engaged with the second output pin and throws off with the first output pin.When latch lever rotated on the second rotational position, latch lever engaged with the first output pin and throws off with the second output pin.

Description of drawings

Here the accompanying drawing that draws just is used for limiting the scope of the invention for explanatory purposes rather than by any way.In the accompanying drawings:

Fig. 1 is schematic diagram, shows the valve lift regulating device of first embodiment of the invention;

Fig. 2 is the sectional elevation that the line II-II along Fig. 1 intercepts;

Fig. 3 is the sectional elevation that the line III-III along Fig. 1 intercepts;

Fig. 4 is the sectional elevation that the line IV-IV along Fig. 1 intercepts;

Fig. 5 is the view of looking along the direction of the arrow V of Fig. 3, shows the first embodiment's valve lift regulating device;

Fig. 6 is the sectional elevation of the first embodiment's actuator;

Fig. 7 is the sectional elevation that the line VII-VII along Fig. 6 intercepts;

Fig. 8 is the sectional elevation that the line VIII-VIII along Fig. 7 intercepts;

Fig. 9 is schematic sectional elevation, and it shows the working state that rotates to the latch lever on the first rotational position from the state of Fig. 7;

Figure 10 is schematic sectional elevation, shows the working state that rotates to the latch lever on the second rotational position from the state of Fig. 7;

Figure 11 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Fig. 1, so that the first output pin is accommodated in the engaging groove of slider;

Figure 12 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Figure 11, so that slider moves on the high engine speed position;

Figure 13 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Figure 12, so that the first output pin is accommodated in the engaging groove of slider;

Figure 14 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Fig. 1, so that the second output pin is accommodated in the engaging groove of slider;

Figure 15 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Figure 14, so that slider moves on the low engine loading position;

Figure 16 is that the valve lift regulating device is in the schematic sectional elevation in such working state, and namely this working state is changed from the state of Figure 15, so that the second output pin is accommodated in the engaging groove of slider;

Figure 17 is the sectional elevation of the actuator of second embodiment of the invention;

Figure 18 is the sectional elevation that the line XVIII-XVIII along Figure 17 intercepts;

Figure 19 is the sectional elevation that the line XIX-XIX along Figure 17 intercepts;

Figure 20 is schematic sectional elevation, shows the working state that rotates to the latch lever on the first rotational position from the state of Figure 17;

Figure 21 is schematic sectional elevation, shows the working state that rotates to the latch lever on the second rotational position from the state of Figure 17;

Figure 22 is the sectional elevation of the actuator of third embodiment of the invention;

Figure 23 is the sectional elevation of the actuator of fourth embodiment of the invention;

Figure 24 is the sectional elevation of the actuator of fifth embodiment of the invention;

Figure 25 is the sectional elevation along the second output pin length actuator that intercept, the 5th embodiment;

Figure 26 is the sectional elevation along the first output pin length actuator that intercept, sixth embodiment of the invention;

Figure 27 is the sectional elevation along the second output pin length actuator that intercept, the 6th embodiment;

Figure 28 is the sectional elevation along the first output pin length actuator that intercept, seventh embodiment of the invention;

Figure 29 is the sectional elevation along the second output pin length actuator that intercept, the 7th embodiment;

Figure 30 is the sectional elevation along the first output pin length actuator that intercept, eighth embodiment of the invention;

Figure 31 is the sectional elevation along the second output pin length actuator that intercept, the 8th embodiment;

Figure 32 is the sectional elevation along the first output pin length actuator that intercept, ninth embodiment of the invention; And

Figure 33 is the sectional elevation along the second output pin length actuator that intercept, the 9th embodiment.

Embodiment

Various embodiments with reference to the accompanying drawings to describe the present invention.Below these embodiments in the discussion, identical part represents with same numeral and for not being repeated in this description for simplicity.

(the first embodiment)

Fig. 1 shows the actuator of first embodiment of the invention.Actuator 70 is applied on the valve lift regulating device (as variable valve gear) 20 of valve system 10, and the intake valve 44 of this valve system 10 driving machine motor-cars (for example automobile) internal-combustion engine is to open and close intake valve 44.Valve lift controlling device 20 is variable valve actuator for air of cam profile conversion hysteria.Each intake valve 44 is as engine valve of the present invention.

With reference to Fig. 1-5, valve lift regulating device 20 comprises low engine speed cam 25, high engine speed cam 30, low engine loading cam 35, slider 50 and actuator 70.Slider 50 is as cam-operated of the present invention.

It is an independent part that low engine speed cam 25, high engine speed cam 30, low engine loading cam 35 and slider 50 are integrally formed.

Low engine speed 25 is disk cams, and this disk cam has internal spline 25a (referring to Fig. 2) in inner edge surface.The internal spline 25a of low engine speed cam 25 is coupled on the external splines 11a of camshaft 11 by this way, and namely it is so that low engine speed cam 25 axially can endwisely slip along camshaft 11 along camshaft 11.Low engine speed cam 25 can be delivered to camshaft 11 to rotation and can axially move with respect to camshaft 11.The lug boss 27 of cam is formed in the outer boundary walls of low engine speed cam 25, so the lug boss 27 of cam is along radially stretching out a prearranging quatity from basic circle 26.Low engine speed cam 25 matches with roller Rocker arm 40, and to form low engine speed cam mechanism, this mechanism converts rotatablely moving of camshaft 11 to the straight reciprocating motion of intake valve 44.In low engine speed cam mechanism, low engine speed cam 25 works to do driver, and roller Rocker arm 40 plays a part driven member.

High engine speed cam 30 is disk cams, and it has internal spline 30a, and this internal spline is coupled among the external splines 11a of camshaft 11 by this way, and namely it makes high engine speed cam 30 axially endwisely slipping along camshaft 11 along camshaft 11.High engine speed cam 30 is along axially being arranged to contiguous low engine speed cam 25.High engine speed cam 30 can be delivered to rotation in the camshaft 11, and can axial motion with respect to cam 11.The lug boss 32 of cam is formed in the outer boundary walls of high engine speed cam 30, so the lug boss 32 of cam is from basic circle 31 along extending radially out a prearranging quatity.The outer surface of the outer surface of basic circle 26 and basic circle 31 seamlessly and smoothly interconnects in the situation that do not form stepped part between them.

The cam profile of high engine speed cam 30 is different from the profile line of low engine speed cam 25.For example, the maximum lift of high engine speed cam 30 (being also referred to as the maximum cam lift) is greater than the maximum lift of low engine speed cam 25.The operating angle of high engine speed cam 30 (being also referred to as the cam work angle) is greater than the operating angle of low engine speed cam 25.High engine speed cam 30 matches with roller Rocker arm 40, thereby forms the high engine speed cam mechanism, and this mechanism converts rotatablely moving of camshaft 11 to the linear reciprocating motion of intake valve 44.In the high engine speed cam mechanism, high engine speed cam 30 plays a part driver, and roller Rocker arm 40 plays a part driven member.

Low engine speed cam 35 is disk cams, it has internal spline 35a, this internal spline is coupled among the external splines 11a of camshaft 11 by this way, and namely it makes low engine loading cam 35 axially endwisely slipping along camshaft 11 along camshaft 11.Low engine loading cam 35 is arranged to contiguous low engine speed cam 25 at the sidepiece of low engine speed cam 25, and this cam 25 is axially relative with high engine speed cam 30 along camshaft 11.Low engine loading cam 35 can be delivered to rotation in the camshaft 11, and can move axially with respect to camshaft 11.The outer boundary walls of low engine loading cam 35 has formed basic circle 36, but does not form the lug boss of cam.More particularly, the cam profile of low engine loading cam 35 is circular, and the cam lift of therefore low engine loading cam 35 is 0.The outer surface of basic circle 36 is not forming in the stepped part situation with respect to the outer surface of basic circle 26 and the outer surface of basic circle 31, seamlessly and smoothly is connected with the outer surface of basic circle 26 and the outer surface of basic circle 31.Low engine loading cam 35 matches with roller Rocker arm 40, forming low engine loading cam mechanism, what this mechanism did not cause intake valve 44 opens motion and closing movement, namely, even when camshaft 11 was rotated, this mechanism stopped the cylinder of motor.

Cam

30,25,35 and slider 50 be positioned under the locational state of axial centre, as shown in Figure 1, the roller 42 of low engine speed cam 25 contact roller Rocker arm 4s 0.

Cam

30,25,35 and slider 50 be in axial position under this state and be called low engine speed position.

In addition,

cam

30,25,35 and slider 50 be under another state on the axial sidepiece (left side shown in Figure 12) of central position, the roller 42 of high engine speed cam 30 contact roller Rocker arm 4s 0, as shown in Figure 12.

Cam

30,25,35 and slider 50 axial position in this state be called the high engine speed position.

In addition,

cam

30,25,35 and slider 50 be positioned under another state on another axial sidepiece (right side shown in Figure 15) of central position, the roller 42 of low engine loading cam 35 contact roller Rocker arm 4s 0, as shown in Figure 15.

Cam

30,25,35 and slider 50 axial position in this state be called low engine loading position.

Slider 50 is formed the cylindrical tube-shaped shape, and is arranged on the axial sidepiece of low engine loading cam 35, and this load cam 35 is relative along the axial and low engine speed cam 25 of camshaft 11.Slider 50 is coupled on the camshaft 11, so slider 50 can be delivered to rotation on the camshaft 11, and can move axially with respect to camshaft 11.Slider 50 can move with

cam

30,25,35 between high engine speed position and low engine loading position with being integral.Low engine speed position is such working position, and namely on this working position, intake valve 44 is coupled with low engine speed cam 25.The high engine speed position is such working position, and namely on this position, intake valve 44 is coupled with high engine speed cam 30.Low engine loading position is such working position, and namely on this position, the opening and closing campaign of intake valve 40 has been stopped.When slider 50 during along axial motion,

cam

30,25,35 and slider 50 move with being integral.

Engaging groove 51 is formed in the outer boundary walls of slider 50, and circumferentially extends along the circumferencial direction of slider 50.In the present embodiment, the axial width along the axial measured engaging groove 51 of camshaft 11 is basically constant along the whole circumferential zones of engaging groove 51 along the circumferencial direction of slider 50.In addition, engaging groove 51 extends along being substantially perpendicular to slider 50 axial directions.The madial wall that is arranged on the engaging groove 51 on the axial sidepiece (left side of Fig. 1) is the first wall 52 of engaging groove 51.Being arranged on another madial wall on this another axial sidepiece (right side of Fig. 1), engaging groove 51 is the second wall 53 of engaging groove 51.First wall 52 has formed the first protuberance 54.The first protuberance 54 so forms, so that along axially increasing towards circumferential side portion towards the second wall 53 overhangs that stretch out, the first protuberance 54, this circumferential side portion is relative with the sense of rotation (driving direction) of slider 50.The second wall 53 has formed the second protuberance 58.The second protuberance 58 is so formed, so that along axially increasing towards circumferential side portion towards first wall 52 overhangs that stretch out, the second protuberance 58, this circumferential side portion is relative with the sense of rotation (driving direction) of slider 50.

The diapire of engaging groove 51 has the first rise surface (the first surface along the radially outward rising) the 64 and second rise surface (the second surface along the radially outward rising) 66.The first rise surface 64 is inclined surfaces, this inclined surface has the degree of depth that reduces, and this degree of depth is radially measured and rear end (tail end) 57 along the circumferencial direction of slider 50 towards the first protuberance 54 reduces from the outer edge surface 68 of slider 50 along slider 50.Rear end 57 is along the rear end of the sense of rotation of slider 50 (driving direction) in the first protuberance 54.The second rise surface 66 is inclined surfaces, and this surface has such degree of depth that reduces, and this degree of depth is along radially measuring and rear end (tail end) 61 along circumferencial direction towards the second protuberance 58 reduces from the outer edge surface 68 of slider 50.Rear end 61 is to be tail end along the rear end of the sense of rotation of slider 50 (driving direction) in the second protuberance 58.

With reference to Fig. 1 and 6-10, actuator 70 is solenoid actuators and comprises housing 71, the first removable pin 80, the second removable pin 83, latch lever 90, driver element 100, the first spring 98, the second spring 99, the first output pin 105, the first delivery spring 109, the second output pin 110 and the second delivery spring 114.

Housing 71 comprises the first supporting part 76 and the second supporting part 79.The first supporting part 76 comprises support 72 and cover 75.Support 72 is configured to the U-shaped shape, and cover 75 is fixed on the support 72.Support 72 is fixed on the cylinder cap 12.

The first removable pin 80 comprises axle 81 and flange 82.Axle 81 is supported by this way by cover 75, and namely this mode is so that axle 81 can axially moving back and forth along the first removable pin 80.Flange 82 forms one at axial end and the axle 81 of axle 81, and this axial end is relative with the bottom 73 of support 72.Flange 82 is radially protruding from the axial end of axle 81 along the first removable pin 80.Flange 82 is as the first protuberance of the present invention.

The second removable pin 83 comprises axle 84 and flange 85.Axle 84 75 supports by this way by cover, namely this mode so that axle 84 along the second removable pin 83 axially can to-and-fro motion.Flange 85 forms one at axial end and the axle 84 of axle 84, and this axial end is relative with the bottom 73 of support 72.Flange 85 is radially protruding from the axial end of axle 84 along the second removable pin 83.In the present embodiment, the first removable pin 80 and the second removable pin 83 are arranged to basically be parallel to each other.Flange 85 is as the second protuberance of the present invention.

Engaging groove 94 is formed in the end 91 of latch lever 90, and the flange 82 of the first removable pin 80 is installed in the engaging groove 94.In addition, engaging groove 95 is formed in the other end 92 of latch lever 90, and this end 92 is vertically relative with end 91 along latch lever 90, and the flange 85 of the second removable pin 83 is installed in the engaging groove 95.Latch lever 90 bridge joints are between the first removable pin 80 and the second removable pin 83.Engaging groove 94 is as the 3rd anastomosis part of the present invention, and engaging groove 95 is as the 4th anastomosis part of the present invention.The intermediate portion 93 that vertically is arranged on the latch lever 90 between an end 91 and the other end 92 along latch lever 90 has through hole 96.Come the protuberance 74 of containment bracket 72 by through hole 96.Latch lever 90 supports by protuberance 74 by through hole 96 by this way, namely this mode so that latch lever 90 can rotate around through hole 96.The spin axis φ of latch lever 90 is between the central axis of the central axis of the first removable pin 80 and the second removable pin 83, and perpendicular to such plane, namely this plane is arranged essentially parallel to the central axis of the first removable pin 80 and the central axis of the second removable pin 83.

Driver element 100 comprises fixed core 101, coil 102, fixed core 103 and coil 104.Fixed core 101 is arranged on the sidepiece of the first removable pin 80, and the bottom 73 of support 72 is arranged on this sidepiece.In addition, fixed core 101 is fixed on the bottom 73 of support 72.Coil 102 comprises wire rod, and this wire rod is wrapped on the radial outside of fixed core 101 with the form of annular.When coil 102 energising (when electric current supply arrives coil 102), coil 102 produces magnetic fields.Fixed core 103 is arranged on the sidepiece of the second removable pin 83, and wherein bottom 78 is arranged in this sidepiece.In addition, fixed core 103 is fixed on the bottom 73 of support 72.Coil 104 comprises wire rod, and this wire rod is wrapped on the radial outside of fixed core 103 in the mode of annular.When coil 104 energising, coil 104 produces magnetic field.Fixed core 101 is as the second fixed core of the present invention, and fixed core 103 is as the 3rd fixed core of the present invention.Coil 102 is as the second coil of the present invention, and coil 104 is as tertiary coil of the present invention.

Drive unit 100 makes fixed core 101 magnetization by the magnetic field that is produced by coil 102 when coil 102 is switched on.When fixed core 101 is magnetized by this way, the first removable pin 80 is attracted to this axial sidepiece by magnetic force, namely be attracted to fixed core 101, so latch lever 90 is along a sense of rotation (counter clockwise direction among Fig. 9) rotation, as shown in Figure 9.

In addition, driver element 100 makes fixed core 103 magnetization by the magnetic field that is produced by coil 104 when coil 104 is switched on.When fixed core 103 is magnetized in this mode, the second removable pin 83 is attracted to this axial sidepiece by magnetic force, namely be attracted to fixed core 103, therefore latch lever 90 is rotated along another sense of rotation (clockwise direction of Figure 10), sense of rotation of this this another sense of rotation and this is opposite, as shown in Figure 10.

In addition, by giving simultaneously coil 102 and coil 104 energisings, driver element 100 can produce heat by coil 102,104, with heated shell 71.

The first spring 98 is arranged between the flange 82 of cover the 75 and first removable pin 80.The first spring 98 is pushed the first removable pin 80 to this another axial sidepiece (the top sidepiece of Figure 10), so that latch lever 90 is rotated along this another sense of rotation (clockwise direction among Figure 10).

The second spring 99 is arranged between the flange 85 of cover the 75 and second removable pin 83.The second spring 99 axially promotes the second removable pin 83 along this another, so that latch lever 90 is rotated along this sense of rotation (counter clockwise direction among Fig. 9).

Latch lever 90 can rotate between neutral position, the first rotational position and the second rotational position.The neutral position is such position, namely on this position, and the mutual balance of thrust of the thrust of the first spring 98 and the second spring 99, as shown in Figure 1.On the neutral position, latch lever 90 engages with the first output pin 105 and the second output pin 110.

The first rotational position is such position, and namely it arrives along this sense of rotation (counter clockwise direction of Fig. 9) from the neutral position when latch lever 90 is rotated, as shown in Figure 9.On the first rotational position, latch lever 90 engages with the second output pin 110 and throws off mutually with the first output pin 105.

The second rotational position is such position, and namely it arrives along this another sense of rotation (clockwise direction of Figure 10) from the neutral position when latch lever 90 is rotated, as shown in Figure 10.On the second rotational position, latch lever 90 engages with the first output pin 105 and throws off mutually with the second output pin 110.

When latch lever 90 is on the neutral position, the flange 82 of the first removable pin 80 is pushed against on a part of inwall (top of Fig. 7) of engaging groove 94, this part inwall is arranged on this another axial sidepiece (the top sidepiece of Fig. 7).Therefore, form the gap between a part of inwall (bottom of Fig. 7) of flange 82 and engaging groove 94, this part inwall is arranged on this axial sidepiece (downside of Fig. 7).In addition, when latch lever 90 is in the neutral position, the flange 85 of the second removable pin 83 is pushed against on a part of inwall (top of Fig. 7) of engaging groove 95, this part inwall is arranged on this another axial sidepiece (upside of Fig. 7).Therefore, form the gap between a part of inwall (bottom of Fig. 7) of flange 85 and engaging groove 95, this part inwall is arranged on this axial sidepiece (downside of Fig. 7), as preferably as shown in Figure 8.

The spin axis φ that axially is arranged essentially parallel to latch lever 90 of the first output pin 105 and radially consistent with slider 50 basically.The first output pin 105 is supported by the second supporting portion 79 of housing 71 by two

bearings

86,87 by this way, this mode so that the first output pin 105 along it axially can to-and-fro motion.That is, the first output pin 105 so arranges, so that the axial and imaginary plane of the first output pin 105 is crossing, and this imaginary plane comprises the sense of rotation (more particularly, being this sense of rotation and this another sense of rotation) of latch lever 90.More particularly, in particular cases this, the first output pin 105 so arranges, thus the first output pin 105 axially be substantially perpendicular to imaginary plane.The second supporting portion 79 has the first supported hole 790, the first output pins 105 and holds by this first supported hole 790.

Bearing

86,87 is fixed on the inwall of the first supported hole 790.

The first output pin 105 has the first circular groove 106, and this first circular groove 106 is along radially inwardly being recessed into and extending along circumferencial direction in the first output pin 105.When latch lever 90 was placed on the neutral position of latch lever 90, the first circular groove 106 of the first output pin 105 engaged the intermediate portion 93 of latch levers 90.When the first circular groove 106 engaged the intermediate portion 93 of latch lever 90, the axial motion of the first output pin 105 was restricted in the relevant position of the first output pin 105, and on this relevant position, the first output pin 105 separates with slider 50.

The first output pin 105 has formed the first taper protuberance 107, this protuberance 107 on axial position along extending radially out, this axial position along the first output pin 105 axially between bearing 86 and bearing 87.The external diameter of the first taper protuberance 107 axially reduces towards slider 50 along the first output pin 105.The first delivery spring 109 is arranged on the axial sidepiece of the first taper protuberance 107, and this axial sidepiece is axially opposite with slider 50 along the first output pin 105.The first delivery spring 109 is pushed the first output pin 105 to slider 50 sides.When latch lever 90 is placed on the first rotational position the first output pin 105 from the intermediate portion 93 of latch lever 90, discharge, when throwing off with it, the first output pin 105 by the thrust of the first delivery spring 109 towards slider 50 side shafts to movement.The first taper protuberance 107 plays a part spring guide.

The second supporting portion 79 has the first conical surface 77, and this conical surface is on the slider that axially is positioned at the first taper protuberance 107 50 sides of the first output pin 105.The internal diameter of the first conical surface 77 axially reduces towards slider 50 sides along the first output pin 105.At the first output pin 105 after latch lever 90 is thrown off, when the first output pin 105 during along axially the moving towards slider 50 sides of the first output pin 105, the first conical surface 77 and the first taper protuberance 107 formation surface-p-Surface Contacts.

When the first output pin 105 during along axially the moving towards slider 50 sides of the first output pin 105, the first output pin 105 is installed in the engaging groove 51.When the first output pin 105 is accommodated in engaging groove 51 when interior, the first output pin 105 engages with the inwall of engaging groove 51 and the therefore axial position of limit slippage device 50.More particularly, during slider 50 is rotated, cam 30,25,35 and slider 50 place under the low locational state of engine speed, when the first output pin 105 engages with the first inclined surface 55 of the first protuberance 54, the first output pin 105 is driven into slider 50 on the high engine speed position, wherein, this first inclined surface is arranged on the front side, is the front sidepiece along the sense of rotation of slider 50.In addition, during slider 50 is rotated, cam 30,25,35 and slider 50 be under the locational state of high engine speed, when the first output pin 105 engages with the second inclined surface 59 of the second protuberance 58, the first output pin 105 is driven into slider 50 on the low engine speed position, wherein, this second inclined surface 59 is arranged on the front side, is the front sidepiece along the sense of rotation of slider 50.

The first output pin 105 has the first slidingsurface 108, and this first slidingsurface 108 is arranged on the barrel surface on the axial sidepiece of the first circular groove 106, and this axial sidepiece is axially opposite with slider 50 along the first output pin 105.The first slidingsurface 108 of the first output pin 105 can contact the intermediate portion 93 of latch lever 90 slidably.When driver element 100 when the first rotational position of latch lever 90 stops the driving of the first removable pin 80, latch lever that the restriction of the first slidingsurface 108 is caused by the thrust of the first spring 98 90 is rotated towards the neutral position.In addition, when the first output pin 105 was pushed against on the first rise surface 64 of slider 50 or the second rise surface 66, the first slidingsurface 108 slided at latch lever 90.Therefore, latch lever 90 is directed in the first circular groove 106.

Axially and basically radially consistent with slider 50 that axially is arranged essentially parallel to the first output pin 105 of the second output pin 110.The second output pin 110 is supported by the second supporting portion 79 of housing 71 by two

bearings

88,89 by this way, this mode so that the second output pin 110 along axially can to-and-fro motion.That is, the second output pin 110 so arranges, so that the axial and imaginary plane of the second output pin 110 is crossing, and this imaginary plane comprises the sense of rotation (more particularly, being this sense of rotation and this another sense of rotation) of latch lever 90.More particularly, in particular cases this, the second output pin 110 so arranges, thus the second output pin 110 axially be substantially perpendicular to imaginary plane.The second supporting portion 79 has the second supported hole 795, the second output pins 110 and holds by this first supported hole 795.

Bearing

88,89 is fixed on the inwall of the second supported hole 795.

The second output pin 110 has the second circular groove 111, and this second circular groove 111 is along radially inwardly being recessed into and extending along circumferencial direction in the second output pin 110.When latch lever 90 was placed on the neutral position of latch lever 90, the second circular groove 111 of the second output pin 110 engaged the intermediate portion 93 of latch levers 90.When the second circular groove 111 engaged the intermediate portion 93 of latch lever 90, the axial motion of the second output pin 110 was restricted in the relevant position of the second output pin 110, and on this relevant position, the second output pin 110 separates with slider 50.

The second output pin 110 has formed the first taper protuberance 112, this protuberance 112 on axial position along extending radially out, this axial position along the second output pin 110 axially between bearing 88 and bearing 89.The external diameter of the second taper protuberance 112 axially reduces towards slider 50 along the second output pin 110.The second delivery spring 114 is arranged on the axial sidepiece of the second taper protuberance 112, and this axial sidepiece is axially opposite with slider 50 along the second output pin 110.The second delivery spring 114 is pushed the second output pin 110 to slider 50 sides.When latch lever 90 is placed on the second rotational position the second output pin 110 from the intermediate portion 93 of latch lever 90, discharge, when throwing off with it, the second output pin 110 by the thrust of the second delivery spring 114 towards slider 50 side shafts to movement.The second taper protuberance 112 plays a part spring guide.

The second supporting portion 79 has the second conical surface 78, and this conical surface is on the slider that axially is positioned at the second taper protuberance 112 50 sides of the second output pin 110.The internal diameter of the second conical surface 78 axially reduces towards slider 50 sides along the second output pin 110.After the second output pin 110 and latch lever 90 are thrown off, when the second output pin 110 during along axially the moving towards slider 50 sides of the second output pin 110, the second conical surface 78 and the second taper protuberance 112 formation surface-p-Surface Contacts.

When the second output pin 110 during along axially the moving towards slider 50 sides of the second output pin 110, the second output pin 110 is installed in the engaging groove 51.When the second output pin 110 is accommodated in engaging groove 51 when interior, the second output pin 110 engages with the inwall of engaging groove 51 and the therefore axial position of limit slippage device 50.More particularly, during slider 50 is rotated,

cam

30,25,35 and slider 50 place under the low locational state of engine speed, when the second output pin 110 engages with the second inclined surface 59 of the first protuberance 54, the second output pin 110 is driven into slider 50 on the low engine speed position, wherein, this second inclined surface is arranged on the front side, is the front sidepiece along the sense of rotation of slider 50.In addition, during slider 50 is rotated,

cam

30,25,35 and slider 50 be under the low locational state of engine loading, when the second output pin 110 engaged with the first inclined surface 55 of the first protuberance 54, the second output pin 110 was driven into slider 50 on the low engine speed position.

The second output pin 110 has the second slidingsurface 113, and this second slidingsurface 113 is arranged on the barrel surface on the axial sidepiece of the second circular groove 111, and this axial sidepiece is axially opposite with slider 50 along the second output pin 110.The second slidingsurface 113 of the second output pin 110 can contact the intermediate portion 93 of latch lever 90 slidably.When driver element 100 when the second rotational position of latch lever 90 stops the driving of the second removable pin 83, latch lever that the restriction of the second slidingsurface 113 is caused by the thrust of the second spring 99 90 is rotated towards the neutral position.In addition, when the second output pin 110 was pushed against on the first rise surface 64 of slider 50 or the second rise surface 66, the second slidingsurface 113 slided at latch lever 90.Therefore, latch lever 90 is directed in the second circular groove 111.

Next, with reference to Fig. 1,7 and 9-16 the work of valve lift regulating device 20 is described.

Be positioned under the low locational Fig. 1 state of engine speed at slider 50, when camshaft 11 rotation, rotatablely moving of low engine speed cam 25 is transmitted to intake valve 44 and therefore is converted into the linear reciprocating motion of intake valve 44 by roller Rocker arm 40.

Under the state of Fig. 1, the latch lever 90 of actuator 70 is positioned on the neutral position, as shown in Figure 7.Under latch lever 90 was positioned at state on the neutral position, the first output pin 105 and the second output pin 110 engaged latch levers 90.Therefore, the axial motion of the axial motion of the first output pin 105 and the second output pin 110 is restricted in the relevant position, and on this phase position, the first output pin 105 and the second output pin 110 separate with slider 50.

During high engine speed scope under arriving Fig. 1 state, when the first output pin 105 was consistent with the position of the first protuberance 54 with respect to the circumferential position of slider 50 along slider 50 circumferencial directions, the driver element 100 of actuator 70 gives coil 102 energisings so that fixed core 101 magnetization.Therefore, the first removable pin 80 is attracted to this axial sidepiece, is fixed core 101 sides by magnetic force, and therefore latch lever 90 is rotated on the first rotational position, as shown in Figure 9.On the first rotational position, latch lever 90 engages with the second output pin 110 and throws off with the first output pin 105.When the first output pin 105 was thrown off with latch lever 90, the thrust of the first delivery spring 109 made the first output pin 105 move axially towards slider 50 sides.Therefore, the first output pin 105 is installed in the engaging groove 51.

Under the first output pin 105 was accommodated in Figure 11 state in the engaging groove 51, when slider 50 was rotated with camshaft 11, the first inclined surface 55 of the first protuberance 54 of slider 50 engaged the first output pin 105.Therefore, the axial position of slider 50 is restricted, and slider 50 slides on the high engine speed position, shown in the arrow A 1 of Figure 11 like that.When slider 50 slided on the high engine speed position, the first rise surface 64 of engaging groove 51 was along promoting radially outwardly the first output pin 105, and therefore the first output pin 105 removed from engaging groove 51.When the first rise surface 64 of slider 50 when promoting the first output pin 105 radially outwardly, the first slidingsurface 108 of the first output pin 105 is directed in the first circular groove 106 in latch lever 90 enterprising line slips and latch lever 90.

Be positioned under the locational Figure 12 state of high engine speed at slider 50, when camshaft 11 rotation, rotatablely moving of high engine speed cam 30 is passed in the intake valve 44 by roller Rocker arm 40, and therefore is converted into the linear reciprocating motion of intake valve 44.Be converted into rotatablely moving of high engine speed cam 30 in the situation of linear reciprocating motion of intake valve 44, the lift of intake valve 44 has increased than the situation of the linear reciprocating motion that rotatablely moving of low engine speed cam 25 is converted into intake valve 44.

When arriving the low engine speed range of Figure 12 state, when the first output pin 105 is consistent with the position of the second protuberance 58 with respect to the circumferential position of slider 50 along the circumferencial direction of slider 50, thereby actuator 70 drives the first output pin 105 the first output pin 105 is arrived in the engaging groove 51.

Slide in state moving device 50 when being rotated with camshaft 11 when be accommodated in Figure 13 in the engaging groove 51 at the first output pin 105, and the second inclined surface 59 of the second protuberance 58 of slider 50 engages with the first output pin 105.Therefore, the axial position of slider 50 is restricted, and reaches slider 50 and slides on the low engine speed position, and is such shown in the arrow A 2 of Figure 13.When slider 50 slided on the low engine speed position, the first output pin 105 was by the second rise surface 66 of engaging groove 51 and along being pushed radially outwardly, and therefore removed from engaging groove 51.

During low engine loading scope under arriving Fig. 1 state, when the second output pin 110 was consistent with the position of the second protuberance 58 with respect to the circumferential position of slider 50 along slider 50 circumferencial directions, the driver element 100 of actuator 70 gives coil 104 energisings so that fixed core 103 magnetization.Therefore, the second removable pin 83 is attracted to this axial sidepiece, is fixed core 103 sides by magnetic force, and therefore latch lever 90 is rotated on the second rotational position, as shown in Figure 10.On the second rotational position, latch lever 90 engages with the first output pin 105 and throws off with the second output pin 110.When the second output pin 110 was thrown off with latch lever 90, the thrust of the second delivery spring 114 made the second output pin 110 move axially towards slider 50 sides.Therefore, the second output pin 110 is installed in the engaging groove 51.

Be accommodated under the state of the Figure 14 in the engaging groove 51 at the second output pin 110, when slider 50 was rotated with camshaft 11, the second inclined surface 59 of the second protuberance 58 of slider 50 engaged the second output pin 110.Therefore, the axial position of slider 50 is restricted, and slider 50 slides on the low engine loading position, shown in the arrow A 3 of Figure 14 like that.When slider 50 slided on the low engine loading position, the second rise surface 66 of engaging groove 51 was along promoting radially outwardly the second output pin 110, and therefore the second output pin 110 removed from engaging groove 51.When the second rise surface 66 of slider 50 when promoting the second output pin 110 radially outwardly, the second slidingsurface 113 of the second output pin 110 is directed in the second circular groove 111 in latch lever 90 enterprising line slips and latch lever 90.

Be positioned at slider 50 under the state of low locational Figure 15 of engine loading, when camshaft 11 rotation, roller Rocker arm 40 is not swung.Therefore, do not produce the opening and closing campaign of intake valve 44.In this mode, respective cylinder has stopped, and therefore fuel consumption improves.In addition, in the situation that hybrid vehicle, regeneration of energy efficient has improved.

Under the state of Figure 15, when outside low engine loading scope, driving motor, when the second output pin 110 is consistent with the position of the first protuberance 54 with respect to the circumferential position of slider 50 along the circumferencial direction of slider 50, thereby driving the second output pin 110, actuator 70 make the second output pin 110 enter into engaging groove 51.

Under the second output pin 110 was contained in Figure 16 state in the engaging groove 51, when slider 50 was rotated with camshaft 11, the first inclined surface 55 of the first protuberance 54 of slider 50 engaged the second output pin 110.Therefore, the axial position of slider 50 is restricted, and reaches slider 50 and slides on the low engine speed position, and is such shown in the arrow A 4 of Figure 16.When slider 50 slides on the low engine speed position, along promoting radially outwardly the second output pin 110, and therefore, the second output pin 110 is removed from engaging groove 51 by the first rise surface 64 of engaging groove 51.

As discussed above such, in the first embodiment's actuator 70, joint between the first output pin 105 and latch lever 90 is released, thereby when the first removable pin 80 is shifted to this axial sidepiece, make the first output pin 105 shift to slider 50, and make the second removable pin 83 shift to this another axial sidepiece.In addition, in actuator 70, joint between the second output pin 110 and latch lever 90 is released, thereby makes the second output pin 110 shift to slider 50 when the first removable pin 80 is shifted to this another axial sidepiece, and makes the second removable pin 83 shift to this axial sidepiece.

Here, it should be noted, when the first removable pin 80 and the second removable pin 83 owing to having applied external vibration and/or exterior vibration and during along its axial vibration, the first removable pin 80 and the second removable pin 83 can move towards common axial sidepiece.Therefore, if be not to shift to separately disalignment to sidepiece at the first removable pin 80 and the second removable pin 83, in the latch lever 90 non-rotary situations, the same with the present embodiment so, it is possible avoiding carrying out wrong rotation by the latch lever 90 that application external vibration and/or exterior vibration cause.

In addition, in the first embodiment, the first output pin 105 and the second output pin 110 are so arranged, so that the first output pin 105 axially and the second output pin 110 axially be substantially perpendicular to imaginary plane, this imaginary plane comprises the sense of rotation (this sense of rotation and this another sense of rotation) of latch lever 90.Therefore, owing to using external vibration and/or exterior vibration and when moving axially, be applied to rotation that power latch lever 90 on can not cause latch lever 90 from the first output pin 105 and the second output pin 110 when the first output pin 105 and the second output pin 110.Therefore, avoiding latch lever 90 is possible by the mistake rotation that application external vibration and/or exterior vibration cause.

Consequently, under the state that driver element 100 is stopped restriction the first output pin 105 and/or the second output pin 110 to move towards slider 50 sides be possible.Therefore, prevent that caused damage is possible on the first output pin 105 and the second output pin 110 by excessive load is applied in actuator 70, wherein this excessive load is owing to following reason causes, and namely the first output pin 105 and the second output pin 110 touch and be different from diverse location engaging groove 51, slider 50.

In addition, in the first embodiment, thereby the first spring 98 promotes the first removable pin 80 latch lever 90 is rotated along this another sense of rotation (clockwise direction of Figure 10).In addition, the second spring 99 promotes the second removable pin 83, thereby latch lever 90 is rotated along this sense of rotation (counter clockwise direction of Fig. 9).Therefore, when driver element 100 makes latch lever 90 along this sense of rotation (counter clockwise direction of Fig. 9) when being rotated, the Driving force of the second spring 99 is applied in to make latch lever 90 to be rotated along this sense of rotation.Consequently, can reduce the working load of driver element 100.In addition, when driver element 100 makes latch lever 90 along this another sense of rotation (clockwise direction of Figure 10) when being rotated, the Driving force of the first spring 98 is applied in to make latch lever 90 to be rotated along this another sense of rotation.Consequently, can reduce the working load of driver element 100.Therefore, the size of driver element 100 can reduce, and therefore the size of actuator 70 can reduce.

In addition, in the first embodiment, under latch lever 90 was positioned at state on the neutral position, the flange 82 of the first removable pin 80 was pushed against on a part of inwall of engaging groove 94 (top of Fig. 7), and this part inwall is positioned on this another axial sidepiece (upside of Fig. 7).Therefore, between the flange 82 of the first removable pin 80 and a part of inwall of engaging groove 94 (bottom of Fig. 7), form the gap, wherein should be positioned on this axial sidepiece (downside of Fig. 7) by part inwall.In addition, when latch lever 90 was on the neutral position, the flange 85 of the second removable pin 83 was pushed against on a part of inwall of engaging groove 95 (top of Fig. 7), and this part inwall is positioned on this another axial sidepiece (upside of Fig. 7).Therefore, form the gap between a part of inwall (bottom of Fig. 7) of flange 85 and engaging groove 95, this part inwall is positioned on this axial sidepiece (downside of Fig. 7).

Therefore, when the first removable pin 80 or the second removable pin 83 are shifted to this axial side (downside of Fig. 9 or Figure 10), owing to existing above-mentioned respective clearance to limit that latch lever 90 is caught (prevention) first removable pin 80 and the second removable pin 83 is possible.In addition, when the first removable pin 80 is shifted to this axial sidepiece (downside of Fig. 9) owing to there being above-mentioned respective clearance so that the travelling speed of the first removable pin 80 can be accelerated be contiguous to time of latch lever 90 at the first removable pin 80 before.Consequently, latch lever 90 can rotate rapidly.In addition, when the second removable pin 83 is shifted to this axial sidepiece (downside of Figure 10) owing to there being above-mentioned respective clearance so that the travelling speed of the second removable pin 83 before the second removable pin 83 is contiguous to time on the latch lever 90, can be accelerated.Consequently, latch lever 90 can fast rotational.

In addition, in the first embodiment, when when the first output pin 105 is thrown off with latch lever 90, the first output pin 105 is when axially shifting to slider 50 side, and the first taper protuberance 107 of the first output pin 105 has formed surface-p-Surface Contact with the first conical surface 77 of housing 71.In addition, when when the second output pin 110 is thrown off with latch lever 90, the second output pin 110 is when axially shifting to slider 50 side, and the second taper protuberance 112 of the second output pin 110 has formed surface-p-Surface Contact with the second conical surface 78 of housing 71.

Consequently, the first output pin 105 and the second output pin 110 each springback capacity from slider 50 can be reduced or minimize after abutting slider 50.Therefore, the first output pin 105 and the second output pin 110 each can be inserted into reliably in the engaging groove 51 of slider 50.

In addition, in the first embodiment, the fixed core 101 of driver element 100 and fixed core 103 form one with the support 72 of housing 71.Therefore, the quantity of part can reduce or minimize.

When the first output pin 105 and the second output pin 110 move with respect to housing 71, enter into the oil of housing 71 inside from slider 50 sides as oiling agent (lubricant oil) by the first supported hole 790 and the second supported hole 795.But under the temperature environment of cold (for example cold winter) condition, because the oil viscosities in the housing 71 increase, therefore the first and second output pins 105, the 110 and first and second

removable pins

80,83 each travelling speeds can adversely reduce.In the first embodiment, in order to solve this shortcoming, therefore switch on simultaneously (can switch on simultaneously) for coil 102 and coil 104 at driver element 100, thereby coil 102 and coil 104 have produced heat and have therefore heated the interior oil of housing 71.Therefore, can prevent that the oily viscosity in the housing 71 from increasing, and therefore can prevent the first and second output pins 105, the 110 and first and second

removable pins

80,83 each travelling speeds reduce.

(the second embodiment)

The actuator of second embodiment of the invention is described with reference to Figure 17-19.

The latch lever 121 of actuator 120 is formed rod.

The first removable pin 125 comprises axle 126 and flange 127.Axle 126 supports by cover 75 by this way, and namely this mode is so that axle 126 axially can move back and forth along the first removable pin 125.Flange 127 forms one with axle 126 on corresponding axial position, this axial position is positioned on fixed core 101 sides of cover 75.Conjugate foramen 128 is formed on the end of axle 126, and this end is relative with driver element 100.One end 122 of latch lever 121 is accommodated in the conjugate foramen 128.The first spring 129 is between the flange 127 and fixed core 101 of the first removable pin 125.The first spring 129 is pushed the first removable pin 125 to this another axial sidepiece (upside of Figure 17).Conjugate foramen 128 is as the first anastomosis part of the present invention.The second removable pin 130 comprises axle 131 and flange 132.Axle 131 supports by cover 75 by this way, and namely this mode is so that axle 131 axially can move back and forth along the second removable pin 130.Flange 132 forms one with axle 131 on corresponding axial position, this axial position is positioned on fixed core 103 sides of cover 75.Conjugate foramen 133 is formed in the end of axle 131, and this end is relative with driver element 100.Along vertically being accommodated in the conjugate foramen 133 with these 122 the other end 123 opposite, latch lever 121, end of latch lever 121.The second spring 134 is between the flange 132 and fixed core 103 of the second removable pin 130.The second spring 134 is pushed the second removable pin 130 to this another axial sidepiece (upside of Figure 17).Conjugate foramen 133 is as the second anastomosis part of the present invention.

When latch lever 121 is positioned on the neutral position, this end 122 of latch lever 121 is pushed against on a part of inwall (bottom of Figure 17) of conjugate foramen 128, and this part inwall axially is positioned on this axial sidepiece (downside of Figure 17) along the first removable pin 125.Therefore, form the gap between a part of inwall (top of Figure 17) of this end 122 of latch lever 121 and conjugate foramen 128, this part inwall is positioned on this another axial sidepiece (upside of Figure 17).In addition, when latch lever 121 was positioned on the neutral position, this other end 123 of latch lever 121 was pushed against on a part of inwall (bottom of Figure 17) of conjugate foramen 133, and this part inwall is positioned on this axial sidepiece (downside of Figure 17).Therefore, form the gap between a part of inwall (top of Figure 17) of this other end 123 of latch lever 121 and conjugate foramen 133, this part inwall is positioned on this another axial sidepiece (upside of Figure 17).

The first output pin 105 and the second output pin 110 are positioned on the axial sidepiece of latch lever 121, and this axial sidepiece is axially relative with driver element 100 along the first removable pin 125.That is, the first output pin 105 and the second output pin 110 are on this another the axial sidepiece (upside of Figure 17) that axially is positioned at latch lever 121 of the first removable pin 125.

Be applied in the thrust of the thrust of the first spring 129 and the second spring 134 with joint efforts latch lever 121 is pushed against on the first output pin 105 and the second output pin 110.

Next, the work of actuator 120 described with reference to Figure 20 and 21.

When making latch lever 121 rotate on the first rotational position (referring to Figure 20) from the neutral position, latch lever 121 is rotated around corresponding fulcrum, and this fulcrum is the intermediate portion 124 of latch lever 121 and the point of contact between the second output pin 110.When making latch lever 121 rotate on the second rotational position (referring to Figure 21) from the neutral position, latch lever 121 is rotated around corresponding fulcrum, and this fulcrum is the intermediate portion 124 of latch lever 121 and the point of contact between the first output pin 105.

In a second embodiment, obtained the advantage similar with the first embodiment.In addition, can avoid when latch lever 121 is rotated latch lever 121 to catch (prevention) first removable pin 125 and the second removable pin 130 owing to there being above-mentioned respective clearance.

(the 3rd embodiment)

The actuator of third embodiment of the invention is described with reference to Figure 22.

The driver element 141 of actuator 140 comprises fixed core 142, coil 143, the first removable pin 144 and the second removable pin 146.Fixed core 142 is positioned at this axial sidepiece (downside of Figure 22) of the first removable pin 44 and the second removable pin 146 and goes up and be fixed on the support 72 of housing 71.Coil 143 comprises wire rod, and this wire rod is wrapped on the radial outside of fixed core 142 with the form of annular.When coil 143 energising (when electric current supply is in the coil 143), coil 143 has produced magnetic field.Fixed core 142 is as the first fixed core of the present invention, and coil 143 is as the first coil of the present invention.

The flange of the first removable pin 144 (as the first permanent magnet) thus 145 be magnetized and form permanent magnet, and the flange of the second removable pin 146 (as the second permanent magnet) 147 also is magnetized, thereby formed permanent magnet.More particularly, the direction of magnetization of flange 145 is consistent with axial (i.e. the movable direction of the first removable pin 144) of the first removable pin 144 in fact.In addition, the polarity that is positioned at the magnetic pole of the flange 145 on fixed core 142 sides is different from the polarity of magnetic pole of the flange 147 of the second removable pin 146 on fixed core 142 sides.The direction of magnetization of the flange 147 of the second removable pin 146 is consistent with axial (i.e. the movable direction of the second removable pin 146) of the second removable pin 146 in fact.For example, the polarity that is positioned at the magnetic pole of the flange 145 on fixed core 142 sides can be the S utmost point, and the polarity that is positioned at the magnetic pole of the flange 147 on fixed core 142 sides can be the N utmost point, and is such as shown in figure 22.

When electric current supplied in the coil 143 along forward direction, the first removable pin 144 attracted on the fixed core 142 by magnetic force.At this moment, fixed core 142 is magnetized by magnetic field along such direction, and namely the flange 145 of this direction and the first removable pin 144 is identical.In addition, when electric current supplied in the coil 143 along opposite direction, the second removable pin 146 attracted on the fixed core 142 by magnetic force, wherein this opposite direction and opposite direction forward.At this moment, fixed core 142 is magnetized by magnetic field along such direction, and namely the flange 147 of this direction and the second removable pin 146 is identical.

In the 3rd embodiment, obtained the advantage similar with the second embodiment.In addition, the number of spare parts of driver element 141 can reduce or be minimized.

(the 4th embodiment)

The actuator of fourth embodiment of the invention is described with reference to Figure 23.

Actuator 150 comprises the heater 151 of heated shell 71.Therefore, under the condition of chilling temperatures environment, prevent that viscosity by the oil of housing 71 inside from increasing the operating rate that reduces actuator 150 that causes, especially preventing that viscosity by the oil of housing 71 inside from increasing minimizing the first output pin 105 of causing and the speed of response of the second output pin 110 is possible.

(the 5th embodiment)

With reference to Figure 24 and 25 actuator according to fifth embodiment of the invention is described.

In actuator 160, such as shown in figure 24, the inwall of the outer wall of the first output pin 105 and the first supported hole 790 limits the first Room 161 along axial the first conical surface 77 sides at the first taper protuberance 107 of the first output pin 105.In addition, the inwall of the outer wall of the first output pin 105 and the first supported hole 790 limits the second Room 162 at the opposite side of the first taper protuberance 107, and this opposite side is axially relative with the first conical surface 77 along the first output pin 105.In addition, such as shown in figure 25, the inwall of the outer wall of the second output pin 110 and the second supported hole 795 limits the 3rd Room 163 along axial the second conical surface 78 sides at the second taper protuberance 112 of the second output pin 110.In addition, the inwall of the outer wall of the second output pin 110 and the second supported hole 795 limits fourth ventricle 164 at the opposite side of the second taper protuberance 112, and this opposite side is axially relative with the second conical surface 78 along the second output pin 110.

The second supporting portion 166 of housing 165 comprises the first through hole 167 and the second through hole 168 (referring to Figure 24).With reference to Figure 24, under the first output pin 105 and state that latch lever 90 engages, the first through hole 167 is connected with the first Room 161, and the second through hole 168 is connected with the second Room 162.The first through hole 167 and the second through hole 168 extend to the outside of the second supporting portion 166 up hill and dale.Under actuator 160 was installed to state in the motor car engine that stops on the horizontal plane, the first through hole 167 and the second through hole 168 were along extending to the outside of the second supporting part 166 from the first supported hole 790 with respect to substantially horizontal downward direction down.The first through hole 167 and the second through hole 168 each as first row oilhole of the present invention.

The second supporting portion 166 also comprises third through-hole 169 and fourth hole 170 (referring to Figure 25).With reference to Figure 25, under the second output pin 110 and state that latch lever 90 engages, third through-hole 169 is connected with the 3rd Room 163, and fourth hole 170 is connected with fourth ventricle 164.Third through-hole 169 and fourth hole 170 extend to the outside of the second supporting portion 166 up hill and dale.Under actuator 160 was installed to state in the motor car engine that stops on the horizontal plane, third through-hole 169 and fourth hole 170 were along extending to the outside of the second supporting portion 166 from the second supported hole 795 with respect to substantially horizontal downward direction down.Third through-hole 169 and fourth hole 170 each as second row oilhole of the present invention.

In the 5th embodiment, the oil that enters into first to fourth Room 161-164 from slider 50 sides by the first supported hole 790 and the second supported hole 795 can be discharged from housing 165 by first to fourth through hole 167-170.Therefore, preventing from being stored in oil among the first to fourth Room 161-164, to cause the variation of the operating time of operating time of the first output pin 105 and the second output pin 110 be possible.Therefore, can be controlled at easily the conversion timing of changing between these

cams

30,25,35.

In addition, in the 5th embodiment, when the first output pin 105 was shifted to slider 50 side, the fluid in the first Room 161 was discharged in the outside by the first through hole 167.Therefore, it is possible avoiding the motion of flow interference the first output pin 105 in the first Room 161.

In addition, in the 5th embodiment, when the second output pin 110 was shifted to slider 50 side, the fluid in the 3rd Room 163 was discharged in the outside by third through-hole 169.Therefore, it is possible avoiding the motion of flow interference the second output pin 110 in the 3rd Room 163.

In addition, according to the 5th embodiment, under actuator 160 was installed to state in the motor car engine that stops on the horizontal plane, first to fourth through hole 167-170 was along extending with respect to substantially horizontal downward direction down.Therefore, the oil among the first to fourth Room 161-164 can be discharged from housing 165 reliably.

(the 6th embodiment)

With reference to Figure 26 and 27 actuator according to sixth embodiment of the invention is described.

In actuator 180, when the first output pin 105 engaged with latch lever 90, the second through hole 183 of the second supporting portion 182 of housing 181 was connected with the first Room 161 and the second Room 162.In addition, when the second output pin 110 engaged with latch lever 90, the fourth hole 184 of the second supporting portion 182 was connected with the 3rd Room 163 and fourth ventricle 164.

According to the 6th embodiment, can obtain the advantage similar with the 5th embodiment.

In addition, in the 6th embodiment, when the first output pin 105 began to slider 50 lateral movement, the fluid in the first Room 161 was discharged in the outside by the first through hole 167 and the second through hole 183, and each is used as first row oilhole of the present invention this first through hole and the second through hole.Therefore, can further prevent the motion of flow interference the first output pin 105 in the first Room 161.

In addition, in the 6th embodiment, when the second output pin 110 began towards the motion of slider 50 sides, the fluid in the 3rd Room 163 was discharged in the outside by third through-hole 169 and fourth hole 184, this third through-hole and fourth hole each as second row oilhole of the present invention.Therefore, can further prevent the motion of flow interference the second output pin 110 in the 3rd Room 163.

(the 7th embodiment)

The actuator of seventh embodiment of the invention is described with reference to Figure 28 and 29.

The second supporting portion 192 of the housing 191 of actuator 190 comprises first row oilhole 193 and second row oilhole 194.When the first output pin 105 engaged with latch lever 90, first row oilhole 193 was connected with the first Room 161 and the second Room 162.In addition, when the second output pin 110 engaged with latch lever 90, second row oilhole 194 was connected with the 3rd Room 163 and fourth ventricle 164.Under actuator 190 was installed to state in the motor car engine that stops on the horizontal plane, first row oilhole 193 and second row oilhole 194 were along extending with respect to substantially horizontal downward direction down.

According to the 7th embodiment, can obtain the advantage similar with the 5th embodiment.

(the 8th embodiment)

The actuator of eighth embodiment of the invention is described with reference to Figure 30 and 31.

The second supporting portion 202 of the housing 201 of actuator 200 comprises first row oilhole 203 and second row oilhole 204.When the first output pin 105 engaged with latch lever 90, first row oilhole 203 was connected with the first Room 161.In addition, when the second output pin 110 engaged with latch lever 90, second row oilhole 204 was connected with the 3rd Room 163.Under actuator 200 was installed to state in the motor car engine that stops on the horizontal plane, first row oilhole 203 and second row oilhole 204 were along extending with respect to substantially horizontal downward direction down.

According to the 8th embodiment, can obtain the advantage similar with the 5th embodiment.

(the 9th embodiment)

The actuator of ninth embodiment of the invention is described with reference to Figure 32 and 33.

The second supporting portion 212 of the housing 211 of actuator 210 comprises first row oilhole 213 and second row oilhole 214.When the first output pin 105 engaged with latch lever 90, first row oilhole 213 was connected with the second Room 162.In addition, when the second output pin 110 engaged with latch lever 90, second row oilhole 214 was connected with fourth ventricle 164.Under actuator 210 was installed to state in the motor car engine that stops on the horizontal plane, first row oilhole 213 and second row oilhole 214 were along extending with respect to substantially horizontal downward direction down.

According to the 9th embodiment, can conveniently be controlled at the conversion timing of changing between these

cams

30,25,30.In addition, the oil among the first to fourth Room 161-164 can be discharged from housing 211 reliably.

Top embodiment's improvement is described now.

In embodiment improvement, the type of the driver element of actuator can not be solenoid type (electromagnetic type) in the above.For example, the driver element of actuator can be piezoelectric type (being the piezoelectricity type driver element).

In another improvement of embodiment, the first removable pin can be not parallel to the second removable pin in the above.

In another improvement of embodiment, the first output pin can be not parallel to the second output pin in the above.

In the above in another improvement of embodiment, the first output pin axially and the second output pin axially can be not orthogonal to imaginary plane, this imaginary plane comprises the sense of rotation of latch lever, as long as the first output pin is axially crossing with the axial and imaginary plane of the second output pin.

In the above in another improvement of embodiment, if desired, the second conical surface of the second taper protuberance of the first conical surface of the first taper protuberance of the first output pin, housing, the second output pin and/or housing is dispensable so, namely can not want.

During another of embodiment improved in the above, end of this of the first removable pin and latch lever was not in the situation that form the gap and can be bonded with each other between them.In addition, this another end of the second removable pin and latch lever is not in the situation that form the gap and can be bonded with each other between them.

In another improvement of embodiment, the first removable pin and latch lever can be bonded with each other, so that latch lever can rotate when being subject to the axial force of the first removable pin in the above.In addition, the second removable pin and latch lever can be bonded with each other, so that latch lever can rotate when being subject to the axial force of the second removable pin.

In another improvement of embodiment, the supporting portion of carrying out the housing of machine can be formed by any other suitable material (for example metal) that is not resin in the above.

In another improvement of embodiment, actuator can be applied in the valve lift regulating device of the valve system that opens and closes engine exhaust port in the above.

In another improvement of embodiment, the application of actuator is not limited to valve system in the above, and this valve system comprises the roller rocking arm.That is, actuator of the present invention can be applied in any other suitable valve system type.

In the above in another improvement of embodiment, need not hang down the engine loading cam, but can use any other suitable cam type, and this cam has difformity (cam profile), and this shape is different from the shape of low engine speed cam and high engine speed cam.

In another improvement of embodiment, cam and slider can form part separately in the above, and these parts that separate with respect to forming with being separated from each other.

In another improvement of embodiment, cam and slider can be connected on the camshaft by any other appropriate device that is not spline (internal spline and external splines) in the above.

In another improvement of embodiment, the cam profile of high engine speed cam can have any suitable difference with respect to the cam profile of low engine speed cam in the above.For example, the high engine speed cam can have different operating angles separately with low engine speed cam, simultaneously realizes identical maximum lift at high engine speed cam and low engine speed cam in each.As alternative, the high engine speed cam can have different maximum lift separately with low engine speed cam, simultaneously realizes identical operating angle at high engine speed cam and low engine speed cam in each.In addition, high engine speed cam and low engine speed cam can have different timing separately for opening and closing valve, realize identical maximum lift and identical operating angle at high engine speed cam and low engine speed cam in each simultaneously.

During another of embodiment improved in the above, the engaging groove of slider can the vicissitudinous axial width of tool, and this width changes along the circumferencial direction of slider.In addition, the engaging groove of slider can be crooked, so that the axial position of engaging groove is along the circumferencial direction change of slider.

In the above in another improvement of embodiment, under actuator was installed to state in the motor car engine that stops on the horizontal plane, the oil drainage hole of the second supporting portion of housing can extend along substantially horizontal or along the upward direction with respect to substantially horizontal.In addition, the quantity of oil drainage hole can change over 3 or more.

The present invention is not limited to top embodiment and these embodiments' improvement.That is, in the situation that do not break away from essence of the present invention, above embodiment and their improvement can further be modified in every way.For example, in the scope of essence of the present invention, any one or a plurality of above embodiment and improve in any one or a plurality of part can with any other one or more above embodiment and improve in any other one or more part combine.

Claims

1. the actuator of an internal-combustion engine variable valve gear, wherein said actuator is configured to limit the axial position of cam control spare (50), described cam control spare mobile with a plurality of cams (25,30,35) that are installed on the camshaft (11) with being integral, and described actuator comprises:

Housing (71,165,181,191,201,211);

The first removable pin (80,125,144), it supports by housing (71,165,181,191,201,211) by this way, and namely this mode is so that the first removable pin (80,125,144) axially can move back and forth along the first removable pin (80,125,144);

The second removable pin (83,130,146), it is arranged to be parallel to substantially the first removable pin (80,125,144), and support by housing (71,165,181,191,201,211) by this way, namely this mode is so that the second removable pin (83,130,146) axially can move back and forth along the second removable pin (83,130,146);

Latch lever (90,121), bridge joint is between the first removable pin (80,125,144) and the second removable pin (83,130,146), and can be around intermediate portion (93, the 124) rotation of latch lever (90,121), wherein said intermediate portion (93,124) is positioned between the first removable pin (80,125,144) and the second removable pin (83,130,146);

Driver element (100,141), it is configured to, along the first removable pin (80,125,144) axially drive the first removable pin (80 towards an axial side, 125,144), thereby make latch lever (90,121) be rotated along a sense of rotation, and also be configured to, along the second removable pin (83,130,146) axially drive the second removable pin (83 towards a described axial side, 130,146), thereby make latch lever (90,121) be rotated along described another sense of rotation, described another sense of rotation is opposite with a described sense of rotation;

The first spring (98,129), it promotes in latch lever (90,121) and the first removable pin (80,125,144) at least one, thereby latch lever (90,121) is rotated along described another sense of rotation;

The second spring (99,134), it promotes in latch lever (90,121) and the second removable pin (83,130,146) at least one, thereby latch lever (90,121) is rotated along a described sense of rotation;

The first output pin (105), it so arranges, so that the axial and imaginary plane of the first output pin (105) intersects, described imaginary plane comprises a described sense of rotation and described another sense of rotation of latch lever (90,121); Wherein:

The first output pin (105) supports by housing (71,165,181,191,201,211) by this way, and namely this mode is so that the first output pin (105) axially moving back and forth along the first output pin (105);

When latch lever (90,121) when being positioned on the neutral position, the first output pin (105) engages with the intermediate portion (93,124) of latch lever (90,121), wherein on described neutral position, the mutual balance of thrust of the thrust of the first spring (98,129) and the second spring (99,134);

When the intermediate portion (93,124) of the first output pin (105) and latch lever (90,121) when engaging, on a position that separates with cam control spare (50), can prevent that the first output pin (105) from axially moving along the first output pin (105);

The first delivery spring (109), its cam control spare (50) of axially the first output pin (105) being pushed to along the first output pin (105) is positioned at wherein a side;

The second output pin (110), it is arranged to be parallel to substantially the first output pin (105), and therefore the second output pin (110) axially intersects with described imaginary plane; Wherein:

The second output pin (110) supports by housing (71,165,181,191,201,211) by this way, namely this mode so that the second output pin (110) axially move back and forth along the second output pin (110);

When latch lever (90,121) when being positioned on the neutral position, the second output pin (110) engages with the intermediate portion (93,124) of latch lever (90,121);

When the intermediate portion (93,124) of the second output pin (110) and latch lever (90,121) when engaging, prevent that in a position that separates with cam control spare (50) the second output pin (110) from axially moving along the second output pin (110); And

The second delivery spring (114), its cam control spare (50) of axially the second output pin (110) being pushed to along the second output pin (110) is positioned at wherein a side;

Latch lever (90,121) can rotate between the first rotational position of removing from the neutral position along a described sense of rotation and the second rotational position of removing from the neutral position along described another sense of rotation;

When latch lever (90,121) rotated on the first rotational position, latch lever (90,121) engaged with the second output pin (110) and throws off with the first output pin (105); And

When latch lever (90,121) rotated on the second rotational position, latch lever (90,121) engaged with the first output pin (105) and throws off with the second output pin (110).

2. actuator according to claim 1 is characterized in that:

The first output pin (105) and the second output pin (110) are on described another axial side that is axially disposed within latch lever (121) of the first removable pin (80,125,144), and axially relative with a described axial side along the first removable pin (80,125,144) of described another axial side;

Be applied in the thrust of the thrust of the first spring (129) and the second spring (134) with joint efforts latch lever (121) is pushed against on the first output pin (105) and the second output pin (110);

When latch lever (121) rotated on the first rotational position from the neutral position, latch lever (121) was rotated around a corresponding fulcrum, and described corresponding fulcrum is the point of contact between intermediate portion (124) and the second output pin (110); And

When latch lever (121) rotated on the second rotational position from the neutral position, latch lever (121) was rotated around a corresponding fulcrum, and described corresponding fulcrum is the point of contact between intermediate portion (124) and the first output pin (105).

3. actuator according to claim 1, it is characterized in that: latch lever (90) is rotatably supported by housing (71,165,181,191,201,211).

4. actuator according to claim 2 is characterized in that:

The first removable pin (125,144) has the first anastomosis part (128), and described the first anastomosis part forms in groove and the hole, and holds an end (122) of latch lever (121);

The first spring (129) is pushed the first removable pin (125,144) to described another axial side, and described another axial side is axially opposite with a described axial side along the first removable pin (125,144);

When latch lever (121) is positioned on the neutral position, a described end (122) of latch lever (121) is pushed against on a part of inwall at the first joining portion (128), described a part of inwall is along the first removable pin (125, axially being positioned on the described axial side 144), and between another part inwall of the described end (122) of latch lever (121) and the first joining portion (128), forming the gap, described another part inwall is along the first removable pin (125, axially being positioned on described another axial side 144);

The second removable pin (130,146) has the second joining portion (133), described the second joining portion forms in groove and the hole, and the other end (123) that holds latch lever (121), described the other end is vertically opposite with a described end (122) of latch lever (121) along latch lever (121);

The second spring (134) is axially pushed the second removable pin (130,146) to described another axial side along the second removable pin (130,146); And

When latch lever (121) is positioned on the neutral position, described the other end (123) of latch lever (121) is pushed against on a part of inwall at the second joining portion (133), described a part of inwall is along the second removable pin (130, axially being positioned on the described axial side 146), and between another part inwall of described the other end (123) of latch lever (121) and the second joining portion (133), forming the gap, described another part inwall is along the second removable pin (130, axially being positioned on described another axial side 146).

5. actuator according to claim 3 is characterized in that:

The first removable pin (80) has the first protuberance (82), and described the first protuberance stretches out along the radially outward of the first removable pin (80);

An end (91) of latch lever (90) has the 3rd joining portion (94), and described the 3rd joining portion forms in groove and the hole, and holds first protuberance (82) of the first removable pin (80);

The first spring (98) is axially pushed the first removable pin (80) to described another axial side along the first removable pin (80);

When latch lever (90) is positioned on the neutral position, first protuberance (82) of the first removable pin (80) is pushed against on a part of inwall at the 3rd joining portion (94), described a part of inwall is on described another axial side of axially being positioned at of the first removable pin (80), and between another part inwall of first protuberance (82) of the first removable pin (80) and the 3rd joining portion (94), forming the gap, described another part inwall is on the described axial side of axially being positioned at of the first removable pin (80);

The second removable pin (83) has the second protuberance (85), and described the second protuberance stretches out along the radially outward of the second removable pin (83);

The other end (92) of latch lever (90) has the 4th joining portion (95), described the 4th joining portion forms in groove and the hole, and the second protuberance (85) that holds the second removable pin (83), wherein said the other end is vertically opposite with a described end (91) of latch lever (90) along latch lever (90);

The second spring (99) is axially pushed the second removable pin (83) to described another axial side along the second removable pin (83);

When latch lever (90) is positioned on the neutral position, second protuberance (85) of the second removable pin (83) is pushed against on a part of inwall at the 4th joining portion (95), described a part of inwall is on described another axial side of axially being positioned at of the second removable pin (83), and between another part inwall of second protuberance (85) of the second removable pin (83) and the 4th joining portion (95), forming the gap, described another part inwall is on the described axial side of axially being positioned at of the second removable pin (83).

6. arbitrary described actuator according to claim 1-5 is characterized in that:

The first output pin (105) has the first taper protuberance (107), described the first taper protuberance is radially protruding from the first output pin (105) along the first output pin (105), and have the external diameter that reduces, described external diameter axially reduces towards cam control spare (50) along the first output pin (105);

Housing (71,165,181,191,201,211) has the first conical surface (77), described the first conical surface is on the sidepiece that axially is positioned at the first taper protuberance (107) of the first output pin (105), and wherein cam control spare (50) is positioned on the sidepiece of described the first taper protuberance;

When the first output pin (105) is thrown off with latch lever (90,121), when the first output pin (105) along the first output pin (105) axially shift to cam control spare (50) time, the first taper protuberance (107) of first conical surface (77) of housing (71,165,181,191,201,211) and the first output pin (105) forms surperficial effects on surface and contacts;

The second output pin (110) has the second taper protuberance (112), described the second taper protuberance is radially protruding from the second output pin (110) along the second output pin (110), and have the external diameter that reduces, described external diameter axially reduces towards cam control spare (50) along the second output pin (110);

Housing (71,165,181,191,201,211) has the second conical surface (78), described the second conical surface is on the sidepiece that axially is positioned at the second taper protuberance (112) of the second output pin (110), and wherein cam control spare (50) is positioned on the sidepiece of described the second taper protuberance;

When the second output pin (110) is thrown off with latch lever (90,121), when the second output pin (110) along the second output pin (110) axially shift to cam control spare (50) time, the second taper protuberance (112) of second conical surface (78) of housing (71,165,181,191,201,211) and the second output pin (110) forms surperficial effects on surface and contacts.

7. arbitrary described actuator is characterized in that according to claim 1-5, and housing (165,191,201,211) has:

The first supporting portion (76), it supports the first removable pin (80) and the second removable pin (83); And

The second supporting portion (166,192,202,212), it supports the first output pin (105) and the second output pin (110); And

The second supporting portion (166,192,202,212) has:

The first supported hole (790), it holds the first output pin (105);

At least one first row oilhole (167,168,193,203,213), it extends to the outside of the second supporting portion (166,192,202,212) up hill and dale from the first supported hole (790);

The second supported hole (795), it holds the second output pin (110); And

At least one second row oilhole (169,170,194,204,214), it extends to the outside of the second supporting portion (166,192,202,212) up hill and dale from the second supported hole (795).

8. actuator according to claim 6 is characterized in that, housing (165,191,201,211) has:

The second supporting portion (166,192,202,212) has:

The first supported hole (790), it holds the first output pin (105);

The second supported hole (795), it holds the second output pin (110); And

9. actuator according to claim 8 is characterized in that,

The inwall of the outer wall of the first output pin (105) and the first supported hole (790) axially limits the first Room (161) in a side of the first taper protuberance (107) along the first output pin (105), and the first conical surface (77) is positioned on the described side;

The inwall of the outer wall of the first output pin (105) and the first supported hole (790) limits the second Room (162) at the opposite side of the first taper protuberance (107), and described opposite side is axially relative with the first conical surface (77) along the first output pin (105);

Described at least one first row oilhole (167,183) comprising:

At least one first through hole, when the first output pin (105) and latch lever (90,121) when engaging, it is connected with the first Room (161); And

At least one second through hole, when the first output pin (105) and latch lever (90,121) when engaging, it is connected with the second Room (162) and the first Room (161);

The inwall of the outer wall of the second output pin (110) and the second supported hole (795) axially limits the 3rd Room (163) in a side of the second taper protuberance (112) along the second output pin (110), and the second conical surface (78) is positioned on the described side;

The inwall of the outer wall of the second output pin (110) and the second supported hole (795) limits fourth ventricle (164) at the opposite side of the second taper protuberance (112), and described opposite side is axially relative with the second conical surface (78) along the second output pin (110); And

Described at least one second row oilhole (169,184) comprising:

At least one third through-hole, when the second output pin (110) and latch lever (90,121) when engaging, it is connected with the 3rd Room (163); And

At least one fourth hole, when the second output pin (110) and latch lever (90,121) when engaging, it is connected with fourth ventricle (164) and the 3rd Room (163).

10. actuator according to claim 7 is characterized in that:

Under actuator was installed to state on the internal-combustion engine, described at least one first row oilhole (183) was along the outside that extends to the second supporting portion (166,192,202,212) with respect to substantially horizontal downward direction down from the first supported hole (790); And

Under actuator was installed to state on the internal-combustion engine, described at least one second row oilhole (184) was along the outside that extends to the second supporting portion (166,192,202,212) with respect to substantially horizontal downward direction down from the second supported hole (795).

11. arbitrary described actuator according to claim 1-5 is characterized in that:

Driver element (141) comprising:

The first fixed core (142), it is arranged on the described axial side of the first removable pin (144) and the second removable pin (146) and is fixed on the housing (71); And

The first coil (143), it comprises wire rod, and described wire rod is wrapped on the radial outside of the first fixed core (142), wherein with the form of annular, when upper to the first coil (143) electric current supply, the first coil (143) has produced magnetic field;

When the first fixed core (142) when being magnetized by magnetic field, wherein said magnetic field is by producing electric current supply along forward direction in the first coil (143), the first removable pin (144) is attracted to the first fixed core (142) by magnetic force; And

When the first fixed core (142) when being magnetized by magnetic field, wherein said magnetic field is by along oppositely to first coil (143) in produce electric current supply opposite with forward direction, and the second removable pin (146) is attracted to the first fixed core (142) by magnetic force.

12. actuator according to claim 11 is characterized in that:

The first removable pin (144) has the first permanent magnet (145), and described the first permanent magnet is magnetized along the direction of magnetization identical with the movable direction of the first removable pin (144);

The second removable pin (146) has the second permanent magnet (147), and described the second permanent magnet is magnetized along the direction of magnetization identical with the movable direction of the second removable pin (146); And

Be different from the polarity that is arranged at the magnetic pole of the first permanent magnet (145) on wherein the described side in the first fixed core (142) in the polarity that the first fixed core (142) is arranged at the magnetic pole of the second permanent magnet (147) on wherein the side.

13. actuator according to claim 11 is characterized in that:

Housing (71) comprises support (72); And

Support (72) and the first fixed core (142) form one.

14. arbitrary described actuator according to claim 1-5 is characterized in that:

Driver element (100) comprising:

The second fixed core (101), it is arranged on the described axial side of the first removable pin (80,125) and is fixed on the housing (71,165,181,191,201,211);

The second coil (102), it comprises wire rod, and described wire rod is wrapped on the radial outside of the second fixed core (101), wherein with the form of annular, when electric current supply is upper to the second coil (102), the second coil (102) had produced magnetic field;

The 3rd fixed core (103), it is arranged on the described axial side of the second removable pin (83,130) and is fixed on the housing (71,165,181,191,201,211); And

Tertiary coil (104), it comprises wire rod, and described wire rod is wrapped on the radial outside of the 3rd fixed core (103), wherein with the form of annular, when electric current supply is upper to tertiary coil (104), tertiary coil (104) had produced magnetic field;

When the second fixed core (101) was magnetized by the magnetic field that is produced by the second coil (102), the first removable pin (80,125) was attracted to the second fixed core (101) by magnetic force; And

When the 3rd fixed core (103) was magnetized by the magnetic field that is produced by tertiary coil (104), the second removable pin (83,130) was attracted to the 3rd fixed core (103) by magnetic force.

15. actuator according to claim 14 is characterized in that:

Housing (71,165,181,191,201,211) comprises support (72); And

Support (72), the second fixed core (101) and the 3rd fixed core (103) form one.

16. actuator according to claim 14 is characterized in that, the second coil (102) and tertiary coil (104) can be switched on simultaneously, with heated shell (71,165,181,191,201,211).

17. arbitrary described actuator is characterized in that according to claim 1-5, also comprises the heater (151) of heated shell (71,165,181,191,201,211).