CN1914408A - Variable valve mechanism - Google Patents
Variable valve mechanism Download PDFInfo
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- CN1914408A CN1914408A CN 200480037308 CN200480037308A CN1914408A CN 1914408 A CN1914408 A CN 1914408A CN 200480037308 CN200480037308 CN 200480037308 CN 200480037308 A CN200480037308 A CN 200480037308A CN 1914408 A CN1914408 A CN 1914408A
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Abstract
A variable valve mechanism (10) for varying the amount of lift and angle of action of a valve body (12) of an internal combustion engine. The variable valve mechanism (10) has a first cam (54) rotating as a crank rotates, transmission members (24, 38) having second cams (32, 34) that oscillate synchronous with the rotation of the first cam (54) and transmit an action force created by the first cam (54) to the valve body (12), a control shaft (40) adjusted to a predetermined rotational position, varying mechanisms (36, 38) for varying the amount of lift and angle of action of the valve body (12) by varying oscillation ranges of the transmission members (24, 38) according to the rotational position of the control shaft (40), a lost-motion spring (60) for urging the transmission members (24, 38) toward the first cam (54) so that the connection between the transmission members (24, 38) and the first cam (54) is maintained, and an assist spring (64) for urging the transmission members (24, 38) against the urging force of the lost-motion spring (60).
Description
Technical field
The present invention relates to a kind of variable valve actuator for air, particularly relate to the variable valve actuator for air of the internal-combustion engine of a kind of working angle that changes the valve of synchronously opening, closing and/or lift amount with the rotation of camshaft.
Background technique
In the prior art, a kind of variable valve actuator for air with following function is disclosed: the lift amount that can change the air door body of synchronously opening, closing with the rotation of camshaft.In this variable valve actuator for air, following structure is disclosed in the Japanese kokai publication hei 7-63023 communique: in the variable valve actuator for air of the lift amount that can change air door body according to the rotational position of eccentric shaft, for the roll-in that can change according to the rotational position of eccentric shaft with the butt position of cam is received on the cam, by pressure spring (sky move spring) to the rocking arm application of force that is provided with roller.Adopt this variable valve actuator for air,, can always keep the mechanical connection state of cam and roller by the effect of pressure spring.
But in the disclosed existing mechanism of Japanese kokai publication hei 7-63023 communique, to the cam one side pair roller application of force, consequently, eccentric shaft is subjected to the power to the certain orientation effect to pressure spring with valve spring.Therefore, the driving torque that requires of the actuator when making the eccentric shaft rotation increases, and the responsiveness that can produce changeable air valve descends, consumes the problem that electric power increases.
And, the variable valve actuator for air of the lift amount of the air door body that can change internal-combustion engine is for example disclosed in the Japanese kokai publication hei 7-293216 communique.Particularly, this variable valve actuator for air has the mechanical mechanism that can change lift amount between air door body and cam.And the structure of this mechanical mechanism is, when Control Shaft during to a direction rotation, changes its state so that the lift amount of air door body increases, and when Control Shaft during to other directions rotations, the lift amount minimizing of air door body.According to this mechanism,, can change the lift amount of air door body arbitrarily by Spin Control axle suitably.
Make the valve spring of air door body and be equipped with usually in the air door body of internal-combustion engine to the valve-closing direction application of force.Therefore, existing variable valve actuator for air is when opening air door body, and the reaction force acts of this valve spring is on the mechanical mechanism between air door body and the cam.And the lift of air door body is big more, and this reaction force is just big more.
For above-mentioned mechanical mechanism, the state when being subjected to big reaction force along with the air door body lift is compared, and is comparatively stable from the mechanics angle under the less state of this reaction force.Therefore, this mechanical mechanism is easy to make state to change to the direction that the lift amount that is produced reduces usually.That is, in above-mentioned Control Shaft, what be easy to transmit is to make the reaction force of mechanical mechanism to the direction of the change of state corresponding with less lift amount.
When the state of Control Shaft is changed, then can't keep the lift amount of air door body rightly.Therefore, in this variable valve actuator for air, require to adopt reaction force irrespectively can make the state of Control Shaft keep certain mechanism with valve spring.
And in the disclosed existing variable valve actuator for air of Japanese kokai publication hei 7-293216 communique, Control Shaft is driven by motor by gear mechanism.And contain worm screw on the running shaft that is installed in motor, and and the worm gear of this worm meshing in this gear mechanism.The gear mechanism that combines by worm and worm wheel, by act between the two bigger frictional force and both bigger gear ratios, realize higher forward efficiency and lower negative efficient.
According to this gear mechanism, the torque that motor produces can be delivered to Control Shaft with higher efficient, and can fully prevent to be delivered on the motor to the input of Control Shaft.Therefore,, can not be subjected to valve spring to influence the accurately state of control Control Shaft of ground, consequently, can accurately control the lift amount of air door body according to above-mentioned existing variable valve actuator for air.
But in the disclosed existing variable valve actuator for air of Japanese kokai publication hei 7-293216 communique, in the time will improving the lift amount of air door body, need the Spin Control axle in order to revolt the reaction force that its lift amount is diminished.Particularly, in this case,, need make Control Shaft to the big direction rotation of lift quantitative change for resistance will make the reaction force of the valve spring that lift amount diminishes.
In order to satisfy this requirement, need make motor produce bigger driving force.Consequently, produce degradation problem under the motor that electric power increases, the volume increase the causes loading property that motor cost rises, motor consumed.And, when this bigger masterpiece is used for Control Shaft, also produce bigger reversing on the Control Shaft.And the transmission of this bigger power can increase the contact load between each gear, produces the problem of quickening its loss.
Summary of the invention
The present invention proposes in order to address the above problem just, its purpose is, in the variable valve actuator for air of the internal-combustion engine of lift amount that can change the valve of synchronously opening, closing and working angle, reduce the desired load of changeable air valve with the rotation of camshaft.
First invention is a kind of variable valve actuator for air, changes the lift amount and the working angle of the air door body of internal-combustion engine, and it has: first cam that rotates along with the rotation of crank; Transferring elements has second cam, and the rotation of this second cam and above-mentioned first cam is synchronously swung, and the force transmission that above-mentioned first cam produces is arrived above-mentioned air door body; Be adjusted to the Control Shaft of the rotational position of regulation; Changeable mechanism changes the hunting range of above-mentioned transferring elements according to the rotational position of above-mentioned Control Shaft, and changes the lift amount and the working angle of above-mentioned air door body; The sky spring of moving makes above-mentioned transferring elements to the above-mentioned first cam application of force, to keep being connected of above-mentioned transferring elements and above-mentioned first cam; And secondary spring, revolt above-mentioned sky move spring active force and to the above-mentioned transferring elements application of force.
Owing to be provided with the empty spring and of moving of resistance, act on the active force of transferring elements thereby can reduce the sky spring of moving to the secondary spring of the transferring elements application of force.Therefore, can easily change the hunting range of transferring elements, reduce the driving torque of the Control Shaft when changing hunting range.So, the responsiveness of changeable air valve can be improved, and lift amount, working angle can be changed instantaneously.And, owing to can reduce the driving torque of Control Shaft, therefore can make actuator's miniaturization of drive controlling axle, and inferior limit ground suppresses the current sinking of actuator.
Second invention is, in the variable valve actuator for air of above-mentioned improvement, described sky is moved direction that spring changes from high-lift amount, the big little lift amount of working angle one side direction, little working angle one side to the lift amount of described air door body and working angle to the described transferring elements application of force, the lift amount of described air door body and working angle are the closer to little lift amount, little working angle one side, and the active force that acts on the described secondary spring on the described transferring elements is big more.
When the sky spring of moving is done the time spent to the active force of transferring elements from high-lift amount, the big little lift amount of working angle one side direction, little working angle one side, be set in more near little lift amount, little working angle one side, then to act on the active force of transferring elements big more for secondary spring, therefore, particularly can be reduced in the driving torque of little lift amount, the Control Shaft when little working angle one side is carried out variable valve-operating.
The 3rd invention is, in the variable valve actuator for air of above-mentioned improvement, have and make the valve spring of described air door body, described secondary spring to the described transferring elements application of force, resistance acts on the active force of the described valve spring on the described transferring elements via described air door body, to the described transferring elements application of force.
Because the active force that the active force of secondary spring is used to offset valve spring, therefore can reduce the active force of the valve spring that acts on transferring elements.Therefore, can easily change the hunting range of transferring elements, and reduce the driving torque of the Control Shaft in the time of can changing hunting range.
The 4th invention is in the variable valve actuator for air of above-mentioned improvement, to have: the actuator that produces the driving force of the rotational position be used to change described Control Shaft; And the gear mechanism between described actuator and described Control Shaft; Link to each other with shared described Control Shaft with a plurality of described transferring elements of the corresponding setting of described air door body of each cylinder; Described sky is moved the active force of spring, described secondary spring and described valve spring via the sense of rotation transmission to described Control Shaft of described transferring elements and described changeable mechanism; On the length direction of described Control Shaft, more away from described gear mechanism, described sky move the active force of spring, described secondary spring and described valve spring be applied to power on the sense of rotation of described Control Shaft make a concerted effort more little.
Because more away from gear mechanism, what act on power on the sense of rotation of Control Shaft makes a concerted effort more for a short time, therefore can reduce to act on the making a concerted effort of power of Control Shaft in the part that the Control Shaft rigidity reduces, thereby can suppress reversing of Control Shaft.
The 5th invention is, and is in the variable valve actuator for air of above-mentioned improvement, on the length direction of described Control Shaft, more away from described gear mechanism, big more to the active force of the described secondary spring of the described transferring elements application of force.
Because more away from gear mechanism, big more to the active force of the secondary spring of the transferring elements application of force, therefore the load of the part secondary spring that reduces the closer to the Control Shaft rigidity is big more.In Control Shaft, though with position that gear mechanism separates on, be easy to twist etc. because of being subjected to the move active force of spring and valve spring of sky, but, therefore can suppress reversing of Control Shaft owing to reduce by secondary spring from the sky active force that spring and valve spring act on Control Shaft of moving.
The 6th invention is, and is in the variable valve actuator for air of above-mentioned improvement, on the length direction of described Control Shaft, more away from described gear mechanism, more little to the move active force of spring of the described sky of the described transferring elements application of force.
Because more away from gear mechanism, more little to the move active force of spring of the sky of the transferring elements application of force, the therefore part that reduces the closer to the rigidity of Control Shaft, the move load of spring of sky is more little.In Control Shaft, though with position that gear mechanism separates on, be easy to twist etc. because of being subjected to the move active force of spring and valve spring of sky, because more away from gear mechanism, more little to the move active force of spring of the sky of the transferring elements application of force, therefore can suppress reversing of Control Shaft.
The 7th invention is a kind of variable valve actuator for air, has the working angle of the air door body that changes internal-combustion engine and/or the function of lift amount, it is characterized in that having: Control Shaft, for a change described working angle and/or lift amount and its state is controlled; Swing arm between cam and air door body, and is swung synchronously with the rotation of cam, thereby this action of cam power is delivered on the described air door body; Changeable mechanism changes the basic relative angle of described swing arm with respect to described air door body according to the state of described Control Shaft; Actuator produces the driving force of the state be used to change described Control Shaft; Gear mechanism is between described actuator and described Control Shaft; And the auxiliary force generating means, described gear mechanism is applied the auxiliary force that makes on the direction that working angle and/or lift amount increase.
By the state of control Control Shaft, change the basic relative angle of swing arm with respect to air door body, consequently, can change the working angle and/or the lift amount of air door body.And, according to the present invention, can be to the auxiliary force that applies between the gear mechanism between actuator and the Control Shaft on the direction that makes working angle and/or lift amount increase.That is,, can apply the auxiliary force of the direction of the power of inevitable negative function on the direction that working angle and/or lift amount diminish to gear mechanism according to the present invention.Therefore according to the present invention, when working angle and/or lift amount increase, the output that actuator should be produced reduces the part of this auxiliary force.
The 8th the invention be, in the variable valve actuator for air of above-mentioned improvement, described gear mechanism comprises interconnected worm and worm wheel, wherein worm screw is positioned at described actuator one side, and worm gear is positioned at described Control Shaft one side; Described auxiliary force is applied to described worm gear or forms on the structure of one with described worm gear.
The auxiliary force that is applied on the gear mechanism can be imposed on worm gear.In this case, when making worm screw when the big direction of working angle and/or lift quantitative change is rotated, can reduce to act on the frictional force between the worm and worm wheel.And the gear mechanism that is combined by worm and worm wheel at coefficient of friction of rest more hour, demonstrates the high more forward efficiency that begins from state of rest.Therefore according to the present invention, can when starting, actuator make Control Shaft to the big direction of working angle and/or lift quantitative change is moved with enough little power.
The 9th invention is, in the variable valve actuator for air of above-mentioned improvement, has the sky spring of moving, make described swing arm to the described cam application of force, to keep the mechanical connection of described swing arm and described gear, require more to produce bigger working angle and/or lift amount, direction that the amount of deformation of spring increases moves to described sky is moved more in described swing arm.
By the sky active force that spring produces of moving, can keep the mechanical connection of swing arm and cam.This sky spring of moving is hindering swing arm application of force on the direction that working angle and/or the big direction of lift quantitative change move.In the present invention, act on the auxiliary force of gear mechanism, as offset this sky move the active force that spring produces power and work.Therefore according to the present invention, can when moving spring, the sky that use has an above-mentioned characteristic make Control Shaft to the big direction of working angle and/or lift quantitative change is changed with less power.
The tenth invention is, in the variable valve actuator for air of above-mentioned improvement, links to each other with shared described Control Shaft with a plurality of described swing arm of the corresponding setting of described air door body of each cylinder; On the length direction of described Control Shaft, more away from described gear mechanism, the move active force of spring of described sky is more little.
Because it is more away from gear mechanism, more little to the move active force of spring of the sky of the transferring elements application of force, therefore more little at the move load of spring of the low more part sky of Control Shaft rigidity.In Control Shaft, though with position that gear mechanism separates on, be easy to twist etc. because of being subjected to the move active force of spring and valve spring of sky, because more away from gear mechanism, more little to the move active force of spring of the sky of the transferring elements application of force, therefore can suppress reversing of Control Shaft.
The 11 invention is a kind of variable valve actuator for air, changes the lift amount and the working angle of the air door body of internal-combustion engine, it is characterized in that having: first cam of rotation along with the crank rotation; Transferring elements has second cam, and the rotation of this second cam and described first cam is swung synchronously, and the force transmission that described first cam is produced arrives described air door body; Be adjusted to the Control Shaft of the rotational position of regulation; Changeable mechanism changes the hunting range of described transferring elements according to the rotational position of described Control Shaft, and changes the lift amount and the working angle of described air door body; The sky spring of moving makes described transferring elements to the described first cam application of force, to keep being connected of described transferring elements and described first cam; And secondary spring, produce and the move active force of active force antagonism of spring of described sky.
Owing to be provided with the secondary spring of the active force that is used to produce the empty spring of moving of resistance, thereby can reduce the move active force of spring of sky.Therefore, can reduce the driving torque of the Control Shaft of transferring elements hunting range when variable.So, the responsiveness of changeable air valve can be improved, and lift amount, working angle can be changed instantaneously.And, owing to can reduce the driving torque of Control Shaft, therefore can make actuator's miniaturization of drive controlling axle, and inferior limit ground suppresses the current sinking of actuator.
Description of drawings
Fig. 1 is the stereogram of major component of the variable valve actuator for air of embodiments of the present invention 1.
Fig. 2 is as the first arm parts of the composed component of variable valve actuator for air shown in Figure 1 and the exploded perspective view of second arm member.
Fig. 3 is the figure of the situation of the variable valve actuator for air of expression embodiments of the present invention 1 when carrying out little lift motion.
Fig. 4 is the figure that the variable valve actuator for air of expression embodiments of the present invention 1 carries out the situation in high-lift when action.
Fig. 5 is the schematic representation of the major component of the variable valve actuator for air that relates to of expression embodiments of the present invention 1.
Fig. 6 is that expression can change the Control Shaft rotational angle theta
cThe time the schematic representation of state of secondary spring.
Fig. 7 is the schematic representation that is used to that the state that is provided with of secondary spring is described and makes the mechanism of Control Shaft rotation.
Fig. 8 is that expression is by being provided with the performance plot of reduction effect that secondary spring reduces the driving torque of motor.
Fig. 9 is the schematic representation that is used to illustrate the variable valve actuator for air of embodiments of the present invention 2.
To be expression constitute the move schematic representation of example of spring of sky by torsion spring to Figure 10.
Figure 11 is the integrally-built figure that is used to illustrate the variable valve actuator for air of embodiment of the present invention 3.
Figure 12 be expression employed gear mechanism that combines by worm and worm wheel in the embodiments of the present invention 3 forward efficiency and its moment rotating speed the figure of relation.
Figure 13 is the figure of stream that is used for illustrating the employed lubricant oil of variable valve actuator for air of embodiments of the present invention 4.
Embodiment
For the present invention is illustrated in more detail, several embodiments of the present invention is described with reference to accompanying drawing.In addition, for the identical reference character of the mark of the similar elements among each figure, and omit repeat specification.And the present invention is not subjected to the qualification of following mode of execution.
Mode of execution 1
Fig. 1 is the stereogram of major component of the variable valve actuator for air 10 of embodiments of the present invention 1.Variable valve actuator for air shown in Figure 1 is the mechanism that is used to drive the air door body of internal-combustion engine.At this, each cylinder of internal-combustion engine has two intake valves and two outlet valves.And, structure shown in Figure 1 as driving device on single cylinder two intake valves or the mechanism of two outlet valves play a role.
Structure shown in Figure 1 has as intake valve or outlet valve and two air door bodies 12 that play a role.On air door body 12, fixed air valve shaft 14 respectively.The end of air valve shaft 14 joins with the pivot that is arranged on rocking arm 16 1 ends.The active force of following valve spring 62 acts on air valve shaft 14, and the air valve shaft 14 by being subjected to this active force is upward to rocking arm 16 application of forces.The other end of rocking arm 16 is rotatably supported by oil tappet 18.Utilize oil tappet 18, adjust the position of rocking arm 16 on short transverse automatically, thereby can adjust the tappet clearance automatically according to oil pressure.
Central part at rocking arm 16 is provided with roller 20.Dispose swing arm 22 on the top of roller 20.Followingly the peripheral structure of swing arm 22 is described with reference to Fig. 2.
Fig. 2 is the exploded perspective view of the first arm parts 24 and second arm member 26.The first arm parts 24 and second arm member 26 all are the main members in the structure shown in Figure 1.As shown in Figure 2, above-mentioned swing arm 22 part that is the first arm parts 24.
That is, as shown in Figure 2, the first arm parts 24 are that one comprises two swing arms 22 and by the parts of the roller bearing surface 28 of their clampings.Two swing arms 22 are distinguished corresponding settings with two air door bodies 12, and are connected respectively on the above-mentioned roller 20 (with reference to Fig. 1).
On the first arm parts 24, be provided with and connect two swing arms 22 and the bearing portion 30 of opening.And, in swing arm 22, on the face that joins with roller 20, be provided with concentric circle portion 32 and press section 34 respectively.Concentric circle portion 32 is arranged to, with the surface of contact and the bearing portion 30 formation concentric circles of roller 20.In addition, press section 34 is arranged to, the closer to the part of its forward end, far away more apart from the distance at the center of bearing portion 30.
Second arm member 26 has non-swing part 36 and oscillating roller portion 38.Non-swing part 36 is provided with through hole, and Control Shaft 40 is inserted in this through hole.And insertion is used for fixing the fixing pin 42 of both relative positions on non-swing part 36 and Control Shaft 40.Therefore, non-swing part 36 and Control Shaft 40 are as the structure of one and play a role.
Oscillating roller portion 38 has two sidewalls 44.These sidewalls 44 are connected on the non-swing part 36 by running shaft 46 free to rotately.And, between two sidewalls 44, be provided with cam abutment roller 48 and slide roller 50.Cam abutment roller 48 and slide roller 50 can freely be rotated under respectively by the state of sidewall 44 clampings.
Above-mentioned Control Shaft 40 is parts that the bearing portion 30 by the first arm parts 24 rotatably keeps.That is, Control Shaft 40 is the parts that should form one under the state that rotatably remains in the bearing portion 30 with non-swing part 36.For satisfying this requirement, non-swing part 36 (i.e. second arm member 26) before fixing with Control Shaft 40, aligned position between two swing arms 22 of the first arm parts 24.Control Shaft 40 under the state of this aligned in position, connects two bearing portions 30 and non-swing part 36 ground and inserts.Afterwards, the fixing pin 42 that is used for fixing Control Shaft 40 and non-swing part 36 is installed.Consequently, the first arm parts 24 can freely rotate around Control Shaft 40, thereby have realized that non-swing part 36 and Control Shaft 40 form one, and the mechanism that can swing with respect to non-swing part 36 of oscillating roller portion 38.
As mentioned above, when the assembling the first arm parts 24 and second arm member 26, at the relative angle of the first arm parts 24 and Control Shaft 40, be that the relative angle of the first arm parts 24 and non-swing part 36 satisfies in the scope of rated condition, the slide roller 50 of oscillating roller portion 38 can be joined with the roller bearing surface 28 of the first arm parts 24.And, when keeping this both contact, in the scope that satisfies the afore mentioned rules condition, make the first arm parts 24 when Control Shaft 40 rotates, slide roller 50 can be rotated along roller bearing surface 28.The variable valve actuator for air of present embodiment makes along with this rotation that air door body 12 is opened, closing motion.And, this action is specifically described hereinafter with reference to Fig. 4 and Fig. 5.
State when Fig. 1 represents according to said sequence assembling the first arm parts 24, second arm member 26 and Control Shaft 40.Under this state, the position limit of the controlled axle 40 in the position of the first arm parts 24 and second arm member 26.Control Shaft 40 to the fixed component of cylinder head etc., to satisfy above-mentioned condition, that is, makes the roller 20 and swing arm 22 butts of rocking arm 16 by not shown bearing fixing.
Be connected with following actuator (motor 66) on the Control Shaft 40.This actuator can make Control Shaft 40 rotate in the angular range of regulation.State representation shown in Figure 1 is adjusted into the scope that satisfies the afore mentioned rules condition by this actuator with the corner of Control Shaft 40, thereby makes slide roller 50 and roller bearing surface 28 butts.
The variable valve actuator for air 10 of present embodiment also has the camshaft 52 that synchronously rotates with bent axle.Be fixed with the cam 54 on the cylinder that is arranged on each internal-combustion engine on the camshaft 52.Under state shown in Figure 1, cam 54 joins with cam abutment roller 48, and restriction oscillating roller portion 38 moves up.That is, under state shown in Figure 1, by the cam abutment roller 48 and the slide roller 50 of oscillating roller portion 38, the roller bearing surface 28 of the first arm parts 24 is realized the mechanical connection state with cam 54.
According to above-mentioned state, along with the rotation of cam 54, when cam nose extruding cam abutment roller 48, this active force is delivered to roller bearing surface 28 by slide roller 50.Slide roller 50 can be rotated on roller bearing surface 28 on one side, continue the force transmission of cam 54 arrived the first arm parts 24 on one side.Consequently, on the first arm parts 24, producing with Control Shaft 40 is the rotation at center, presses down rocking arm 16 by swing arm 22, and air door body 12 is moved to the opening of valves direction.Variable valve actuator for air 10 as mentioned above, is delivered to roller bearing surface 28 with the active force of cam 54 by cam abutment roller 48 and slide roller 50, thereby air door body 12 is moved.
Then, with reference to Fig. 3 and Fig. 4 the action of the variable valve actuator for air 10 of embodiments of the present invention 1 is described.As mentioned above, variable valve actuator for air 30 mechanically passes to roller bearing surface 28 by the active force with cam 54 and drives air door body 12.Therefore, variable valve actuator for air 10 carries out suitable action in order to make air door body 12, must make cam 54 and roller bearing surface 28 keep the mechanical connection state by cam abutment roller 48 and slide roller 50.And, in order to satisfy this requirement, need be to the direction pair roller bearing surface 28 of cam 54, be the first arm parts 24 application of forces.Fig. 3 and the sky shown in Figure 4 spring 60 of moving is the springs that are used to realize this application of force.And as mentioned above, Fig. 3 and valve spring 62 shown in Figure 4 are to be used for to the spring of valve closing direction to the air door body 12 and rocking arm 16 application of forces.
The move upper end of spring 60 of sky is fixed on cylinder head etc.And, sky move spring 60 the lower end to the rearward end application of force of the opposition side of roller bearing surface 28 1 sides that are provided with swing arm 22.Therefore, under this state, move spring 60 of sky draws the active force of the direction (in Fig. 3 and Fig. 4, swing arm 22 is the direction that the center counterclockwise rotates with Control Shaft 40) of the roller bearing surface 28 of swing arm 22 on producing upwards.This application of force as 28 pairs of slide roller of roller bearing surface 50 upwards the application of force power and play a role, be further used as cam abutment roller 48 be pressed in power on the cam 54 and play a role (with reference to Fig. 1 and Fig. 2).Consequently, as shown in Figure 1, variable valve actuator for air 10 can be kept the state of cam 54 and roller bearing surface 28 mechanical connections.
Fig. 3 represents that variable valve actuator for air 10 moves so that air door body 12 produces the situation of less lift.Below this action is called " little lift motion ".Particularly, Fig. 3 (A) is illustrated in the situation that air door body 12 is closed in the little lift motion process, and Fig. 3 (B) is illustrated in the situation that air door body 12 is opened in the little lift motion process.
In Fig. 3 (A), reference character θ
cIt is the parameter of the rotational position of expression Control Shaft 40.Below this parameter is made as " Control Shaft rotational angle theta
c".At this, for convenience, straight line and the vertical angulation that connects the center of the center of Control Shaft 40 and running shaft 46 is defined as the Control Shaft rotational angle theta
cAnd in Fig. 4 (A), reference character θ
AIt is the parameter of the rotational position of expression swing arm 22.Below this parameter is made as " arm rotational angle theta
A".At this for convenience, straight line and the substantially horizontal angulation that connects the center of the front end of swing arm 22 and Control Shaft 40 is defined as the arm rotational angle theta
A
In variable valve actuator for air 10, the rotational position of swing arm 22, be the arm rotational angle theta
AThe position of depending on slide roller 50.And the position of running shaft 46 of oscillating roller portion 38 and the position of cam abutment roller 48 are depended in the position of slide roller 50.And, in the scope that contacts of keeping cam abutment roller 48 and cam 54, along with the counter clockwise direction of running shaft 46 in Fig. 4 rotated, is the Control Shaft rotational angle theta
cDiminish, the position of slide roller 50 upwards changes.Therefore, in variable valve actuator for air 10, produce the Control Shaft rotational angle theta
cMore little, the arm rotational angle theta
AMore little phenomenon.
Under the state shown in Fig. 3 (A), the Control Shaft rotational angle theta
cIn can keeping cam abutment roller 48 and scope that cam 54 contacts, promptly, be almost minimum value above cam abutment roller 48 limiting in the scope that cam 54 moves.Therefore, under the state shown in Fig. 3 (A), the arm rotational angle theta
ABe almost minimum value.Variable valve actuator for air 10, in this case, the substantial middle portion of the concentric circle portion 32 of swing arm 22 and the roller 20 of rocking arm 16 join, and consequently, air door body 12 becomes the valve closed condition.Below, with the arm rotational angle theta of this moment
ABe called " the reference arm rotational angle theta during little lift
A0".As described below, the corner of Control Shaft 40 is locked into the value by operator settings.
When cam 54 when the state shown in Fig. 3 (A) begins to rotate, shown in Fig. 3 (B), cam abutment roller 48 is pushed by cam nose, moves to the direction of Control Shaft 40.Because the distance from the running shaft 46 of oscillating roller portion 38 to slide roller 50 does not change, therefore when cam abutment roller 48 during near Control Shaft 40, the slide roller 50 that roller bearing surface 28 quilts are rotated on its face presses down.Consequently, swing arm 22 is to the arm rotational angle theta
ABecome big direction rotation, swing arm 22 moves to press section 34 with the point of contact of roller 20 from concentric circle portion 32.
When press section 54 soon joined with roller 40 along with the rotation of swing arm 22, air door body 12 was revolted the active force of valve spring 62 and is moved to the opening of valves direction.And, in the arm rotational angle theta
ABecome the peaked moment, produce maximum lift on the air door body 12.When carrying out little lift motion, as mentioned above, the reference arm rotational angle theta
A0Be less value.Therefore, follow the arm rotational angle theta of cam 54 rotations
AMaximum value, when carrying out little lift motion, also become less value.Below this maximum value is made as " the maximum arm rotational angle theta during little lift
AMAX".In the arm rotational angle theta
ABecome maximum arm rotational angle theta
AMAXThe moment, on air door body 12, produce maximum lift.Variable valve actuator for air 10, shown in Fig. 3 (B), the maximum arm rotational angle theta when producing little lift
AMAXThe time, the point of contact of roller 20 and swing arm 22 enters into press section 34 slightly, consequently, produces small lift in the air door body 12.Therefore, adopt variable valve actuator for air 10,, can synchronously make air door body 12 produce less lift with the rotation of cam 54 by carrying out above-mentioned little lift motion.
And, in this case, the active force of cam 54 actual press down air door body 12 during, promptly become along with the rotary valve body 12 of cam 54 non-closed condition during (crank angle amplitude) also become less (following be called this period " working angle ").Therefore, adopt variable valve actuator for air 10,, can reduce the lift amount of air door body 12, also can reduce this working angle simultaneously by carrying out little lift motion.And in this case, along with the unlatching of air door body 12, less valve spring reaction force acts is in swing arm 22.
Fig. 4 represents that variable valve actuator for air 10 moves so that the situation that air door body 12 produces than high-lift.Below this action is called " high-lift action ".Particularly, Fig. 4 (A) is illustrated in the situation that air door body 12 is closed in the high-lift course of action, and Fig. 4 (B) is illustrated in the situation that air door body 12 is opened in the high-lift course of action.
When carrying out the high-lift action, shown in Fig. 4 (A), the Control Shaft rotational angle theta
cBe adjusted to enough big value.Consequently, when carrying out high-lift when action, in the scope that slide roller 50 does not come off from roller abutting part 28, the arm rotational angle theta during non-lift
A, be the reference arm rotational angle theta
A0Become enough big value.Variable valve actuator for air 10 is in this reference arm rotational angle theta
A0The place, the point of contact of swing arm 22 and roller 20 is positioned at the end of concentric circle portion 32.Therefore, when carrying out the high-lift action, air door body 12 is also kept closed condition.
When cam 54 when the state shown in Fig. 4 (A) begins to rotate, shown in Fig. 4 (B), cam abutment roller 48 is pushed by cam nose, thereby swing arm 22 is in the arm rotational angle theta
ABecome on the big direction and be rotated.Consequently, the point of contact of swing arm 22 and roller 20 moves to press section 34 from concentric circle portion 32, and air door body 12 is revolted the reaction force of valve spring 62 and moved to the opening of valves direction.When carrying out the high-lift action, as mentioned above because the reference arm rotational angle theta
A0Be bigger value, therefore the maximum arm rotational angle theta that produces along with the rotation of cam 54
AMAXAlso become bigger value.Variable valve actuator for air 10 is shown in Fig. 4 (B), when producing this maximum arm rotational angle theta
AMAXThe time, roller 20 becomes the position that fully enters into press section 34 with the point of contact of swing arm 22.Therefore adopt variable valve actuator for air 10, when carrying out above-mentioned high-lift action, shown in Fig. 4 (B), air door body 12 is produced than high-lift and big working angle.And in this case, because the lift amount of air door body 12 is big, therefore along with the unlatching of air door body 12, bigger valve spring reaction force acts is in swing arm 22.
The reaction force of the valve spring 62 that produces along with the unlatching of air door body 12 is to the arm rotational angle theta
AThe direction that diminishes is to swing arm 22 application of forces.In other words, this reaction force is to the Control Shaft rotational angle theta
CThe direction that diminishes is to Control Shaft 40 application of forces.That is, in variable valve actuator for air 10, the reaction force that valve spring 62 produces plays a role as the power of the direction rotation that Control Shaft 40 is reduced to working angle and lift amount.
In variable valve actuator for air 10, except the reaction force of above-mentioned valve spring 62, also apply the move active force of spring 60 of sky to Control Shaft 40.And the same with the reaction force of valve spring 62, this active force also acts on the Control Shaft rotational angle theta
COn the direction that diminishes, be on the working angle of air door body 12 and the direction that lift amount diminishes.
The sky active force that spring 62 produces of moving is along with its amount of deformation increases and increases.In the present embodiment, this amount of deformation along with the first arm parts 24 to the arm rotational angle theta
ABecome the rotation of big direction and increase.And according to the structure of present embodiment, the lift amount that air door body 12 produces is big more, the arm rotational angle theta
ABig more.Therefore, in variable valve actuator for air 10, in the process of high-lift running, when air door body 12 is maximum lift, move spring 62 of sky produces king-sized active force (with reference to the move state of spring 60 of the sky among Fig. 4 (B)), consequently, on the little direction of lift amount, king-sized torque is on Control Shaft 40.
As mentioned above, the variable valve actuator for air 10 of present embodiment is by changing the Control Shaft rotational angle theta
CAnd change reference arm rotational angle theta
A0, consequently, can change working angle and lift amount to air door body 12.
Then, the major component of the variable valve actuator for air 10 that present embodiment is related to reference to Fig. 5 describes.As mentioned above, move spring 60 of sky produces the active force of the direction of the roller bearing surface 28 that draws swing arm 22.And as shown in Figure 5, the active force that makes progress that valve spring 62 produces acts on the air valve shaft 14, and 14 pairs of rocking arms of air valve shaft 16 of the active force by being subjected to valve spring 62 are the application of force upwards.And when the rotational position by cam 54 made the roller 20 of rocking arm 16 join with press section 34, the active force of valve spring 62 also acted on the direction of withdrawing roll bearing surface 28.
Therefore, the move active force of spring 60 and the active force of valve spring 62 of sky acts on simultaneously along same direction on the sense of rotation of swing arm 22, swing arm 22 is applied with the active force of the direction (in Fig. 5 for swing arm 22 counterclockwise the direction of rotation) of withdrawing roll bearing surface 28 by these two springs.And the active force of the direction of last withdrawing roll bearing surface 28 is delivered to non-swing part 36 via slide roller 50, oscillating roller portion 38 and running shaft 46.So, non-swing part 36 and form the Control Shaft 40 of one with non-swing part 36, being subjected to Control Shaft 40 is the power of the direction of the counter clockwise direction rotation among the Fig. 5 at center.
Therefore, when making Control Shaft 40 to the Control Shaft rotational angle theta
CWhen the direction that diminishes is rotated, promptly, make Control Shaft 40 when high-lift is moved little lift motion one sideway swivel of a side direction, because the active force of empty move spring 60 and valve spring 62 is with respect to the action direction of the rotation of Control Shaft 40, identical with the sense of rotation of Control Shaft 40, therefore be used to make the torque of Control Shaft 40 rotations less.
On the other hand, when making Control Shaft 40 when little lift motion one side direction high-lift is moved a sideway swivel, because the active force of empty move spring 60 and valve spring 62 is with respect to the action direction of the rotation of Control Shaft 40, opposite with the sense of rotation of Control Shaft 40, therefore in order to make Control Shaft 40 rotations, need bigger torque.
Therefore, in the variable valve actuator for air 10 of present embodiment, as shown in Figure 5, be provided with secondary spring 64, it is with respect to sky the move active force of spring 60 and valve spring 62, the application of force round about.Secondary spring 64 is made of the torsion spring that helps saving the space, near the upper surface butt the running shaft 46 of one end under the compressed state and non-swing part 36, and the other end is fixed.So, the active force of secondary spring 64 acts on and makes among Fig. 5 on the direction that Control Shaft 40 turns clockwise.Therefore, can apply following power to Control Shaft 40 by secondary spring 64: the side's power in the opposite direction with respect to the active force of the rotation of Control Shaft 40 of moving that spring 60 and valve spring 62 produce with sky.
So, can reduce needed torque when making the rotation of Control Shaft 40 clockwise directions among Fig. 5.Therefore, can reduce the driving torque of needed Control Shaft 40 when little lift motion one side direction high-lift is moved a side shifting especially, thus can instantaneous ground drive controlling axle 40.And, by reducing driving torque, can inferior limit ground suppress to be used for the consumption electric power of the actuator of drive controlling axle 40.
Fig. 6 is that expression can change the Control Shaft rotational angle theta
CThe time the schematic representation of state of secondary spring 64.At this, Fig. 6 (A) represents the Control Shaft rotational angle theta
CState when being set in little lift motion one side (little working angle one side), Fig. 6 (B) represents the Control Shaft rotational angle theta
CBe set in the situation of high-lift when moving a side (big working angle one side).
Shown in Fig. 6 (A), with the Control Shaft rotational angle theta
CWhen being set in little lift motion one side, the Control Shaft rotational angle theta
CBecome minimum, secondary spring 64 is farthest compressed.Under this state, the active force of secondary spring 64 becomes maximum, and acts on and make on the direction that Control Shaft 40 turns clockwise, and therefore, the move active force of spring 60 and valve spring 62 of sky is cancelled out each other.Therefore, can reduce and make the driving torque of Control Shaft 40 when high-lift is moved a side (big working angle one side) rotation, from idling conditions or normal operation starting or acceleration the time, can be promptly from little working angle, little lift status transition to big working angle, high-lift state, thereby can improve starting the time or the driven nature in when acceleration.
On the other hand, shown in Fig. 6 (B), with the Control Shaft rotational angle theta
CBe set in high-lift when moving a side, because the Control Shaft rotational angle theta
CBecome maximum, the active force that therefore acts on the secondary spring 64 of Control Shaft 40 diminishes.And, because acting on, the active force of empty move spring 60 and valve spring 62 makes on the direction that Control Shaft 40 is rotated counterclockwise, therefore can inferior limit ground suppress to begin the driving torque of the Control Shaft 40 when little lift motion one side changes from this state.Therefore, move a side in high-lift and also can change working angle, lift amount rapidly with less driving torque.
Fig. 7 is the schematic representation that is used to that the state that is provided with of secondary spring 64 is described and is used to make the mechanism of Control Shaft 40 rotations.As shown in Figure 7, variable valve actuator for air 10 comprises the mechanism that is used to make Control Shaft 40 rotations.In Fig. 7, to express No. 1 and No. 2 these two cylinders, each cylinder has two air door bodies 12 as intake valve or outlet valve.
As shown in Figure 7, on Control Shaft 40, be provided with the spring guide 66 that is used to keep secondary spring 64.Spring guide 66 comprises by a shared bar of two adjacent cylinders, tube material, is fixed on the spring guide cover 68.Spring guide cover 68 is fixed on cylinder head or is used for bearing cap of support and control axle 40 rotatably etc.
Twine the secondary spring 64 of two adjacent cylinders on spring guide 66, an end of each secondary spring 64 inserts and is fixed on the hole that is arranged on spring guide cover 68.And non-swing part 36 butts of the other end of secondary spring 64 and second arm member 26 are to non-swing part 36 application of forces.
Be provided with worm gear 72 in the end of Control Shaft 40.Near the configuration of worm gear 72 is used for the motor 66 of drive controlling axle 40.Be provided with worm screw 76 on the motor shaft 74 of motor 66, worm gear 72 and worm screw 76 are in engagement.Therefore, when making motor shaft 74 rotations, can make Control Shaft 40 rotations by the engagement of worm screw 76 and worm gear 72.Configuration is used to detect the position transducer 78 of the corner of Control Shaft 40 on the end of Control Shaft 40.
As shown in Figure 7, make in the mechanism of Control Shaft 40 rotation in the engagement by worm gear 72 and worm screw 76, the auto-lock function that can utilize worm mechanism remains on predetermined angular with the corner of Control Shaft 40.In this worm mechanism, owing to the flank of tooth slides each other, so the static friction coefficient of the flank of tooth is bigger, and flank of tooth contact load each other is bigger to the influence that driving torque produces.Therefore, when only the active force of free move spring 60 and valve spring 62 acts on the sense of rotation of Control Shaft 40, cause being used to drive the torque increase of worm screw 76 because of the increase of flank of tooth contact load each other.In the present embodiment, owing to, can control to inferior limit the flank of tooth contact load each other of worm gear 72 and worm screw 76,, particularly can significantly reduce starting torque so can significantly reduce the driving torque of Control Shaft 40 by secondary spring 64 is set.
Fig. 8 is expression by the performance plot of the reduction effect of the driving torque that the motor 66 that secondary spring 64 produces is set, and transverse axis is represented the Control Shaft rotational angle theta
C(deg), the longitudinal axis is represented the driving torque of motor 66.Wherein, Fig. 8 represents to make the characteristic of Control Shaft 40 when little lift motion one side direction high-lift is moved a sideway swivel.
In Fig. 8, the characteristic the when characteristic shown in the dotted line is represented secondary spring 64 is not set.Under this state, because the active force of only free move spring 60 and valve spring 62 acts on the sense of rotation of Control Shaft 40, so the driving torque of Control Shaft 40 when little lift motion one side direction high-lift is moved a sideway swivel becomes big.
In Fig. 8, the characteristic the when characteristic shown in the solid line is represented to be provided with secondary spring 64.Therefore, by being set, secondary spring 64 can offset the sky active force of spring 60 and valve spring 62 of moving, so the driving torque of Control Shaft 40 can be reduced to about 1/3 to 1/2.In addition, even when being provided with secondary spring 64, moving a side from high-lift substantially can not increase to the driving torque of little lift motion one side yet.This is because by the driving torque reduction that secondary spring 64 causes is set, mainly be because the contact load decline each other of the flank of tooth of worm mechanism causes.Therefore, the active force of secondary spring 64 is preferably the degree of the flank of tooth contact load each other that can reduce worm mechanism.
As mentioned above, according to mode of execution 1, for revolt sky move spring 60 and valve spring 62 active force and be provided with the secondary spring 64 of the application of force round about, therefore can significantly reduce the driving force that is used to make Control Shaft 40 rotations.So, the responsiveness in the time of can improving drive controlling axle 40 can change valve lift amount, working angle according to operating condition instantaneously.And,, therefore can suppress the wearing and tearing of the flank of tooth owing to can significantly reduce the flank of tooth contact load each other of the worm mechanism that is used for drive controlling axle 40.And then, can make motor 76 miniaturizations of drive controlling axle 40, but and the current sinking of inferior limit ground inhibition motor 76.
In addition, in above-mentioned mode of execution 1, the first arm parts 24 and oscillating roller portion 38 are equivalent to " transferring elements " in the above-mentioned the 1st or the 11st invention, non-swing part 36 and oscillating roller portion 38 are equivalent to " changeable mechanism " in the above-mentioned the 1st or the 11st invention, cam 54 is equivalent to " first cam " in the above-mentioned the 1st or the 11st invention, and concentric circle portion 32 and press section 34 are equivalent to " second cam " in the above-mentioned the 1st or the 11st invention.
Mode of execution 2
Then, embodiments of the present invention 2 are described.Fig. 9 is the schematic representation that is used to illustrate the variable valve actuator for air 10 of mode of execution 2.The basic structure of the variable valve actuator for air 10 of mode of execution 2 is identical with mode of execution 1.
With mode of execution 1 in the same manner, on No. 1～No. 4 each cylinders, be provided with the secondary spring 64 of the driving torque that is used to reduce Control Shaft 40.Mode of execution 2 is considered the distortion of Control Shaft 40, and the active force of each secondary spring 64 is set at different value respectively.
As implement as described in the mode 1, the move active force of spring 60 and valve spring 62 of sky acts on Control Shaft 40 on same sense of rotation.Because a cylinder is provided with a sky move spring 60, two valve spring 62, and therefore, the load that these springs produce acts on the shared Control Shaft of each cylinder 40.
Therefore, Control Shaft 40 such as is made of at situation the tubule of hollow under, by the move active force of spring 60 and valve spring 62 of sky Control Shaft 40 is twisted, Control Shaft 40 deforms on sense of rotation sometimes.At this moment, the rotation of Control Shaft 40 is locked by worm mechanism, and more away from worm mechanism, the rigidity of Control Shaft 40 is low more, and therefore more away from worm gear 72, the amount of deformation of Control Shaft 40 is big more.
So in mode of execution 2, more away from worm gear 72, the active force of secondary spring 64 is big more.That is, when the active force of the secondary spring 64 of No. 1～No. 4 each cylinders shown in Figure 9 is made as P1 number～P4 respectively, set the active force of each secondary spring 64, so that P1 number＞P2 number＞P3 number＞P4 number.At this moment, difference such as the line footpath by making each secondary spring 64, the number of turn, coil diameter can change the active force of each secondary spring 64.And, can change the active force of each secondary spring 64 by making the setting angle difference of the secondary spring 64 in each cylinder, and needn't change the design of secondary spring 64 itself.
Because secondary spring 64 produces and the active force of the active force antagonism of lost motion springs 60 and valve spring 62, therefore away from worm gear 72, for the low more position of the distortion rigidity of sense of rotation, the active force of secondary spring 64 is big more, thereby can suppress reversing of Control Shaft 40.So, can suppress to produce deviation because of the distortion of Control Shaft 40 causes the lift amount of the air door body 12 on each cylinder, valve opening/shut-in time.In addition, in order to suppress the distortion of Control Shaft 40, also can change the move load of spring 60 of sky according to each cylinder, more away from worm gear 72, the move active force of spring 60 of sky is more little.
In addition, in Fig. 9, though represented example at the end of the Control Shaft 40 of four cylinder internal combustion engines configuration worm mechanism, but when configuration worm mechanism between No. 2 cylinders and No. 3 cylinders, because more away from worm mechanism, the active force of secondary spring 64 is big more, so can suppress the distortion of Control Shaft 40.
As mentioned above, according to mode of execution 2, in order to revolt the sky active force of spring 60 and valve spring 62 of moving, and the secondary spring 64 to the opposite direction application of force is set, so can significantly reduce the driving force that is used to make Control Shaft 40 rotations with mode of execution 1 the same ground.And, because big more, so can suppress to cause that because of the move load of spring 60 and valve spring 62 of sky Control Shaft 40 deforms apart from the distance active force far away more, secondary spring 64 of the worm gear 72 of the rotational position that is used to limit Control Shaft 40.Therefore, can suppress the lift amount of each cylinder, the deviation of working angle, thereby can make the air inflow of each cylinder even.So, can prevent that the deterioration of driven nature and output power from reducing.
And, owing to can suppress the distortion of Control Shaft 40, therefore Control Shaft 40 diameters are diminished and become frivolous.So, can reduce the driving torque of motor 66, and realize the miniaturization of internal-combustion engine.
Figure 10 is illustrated in the above-mentioned mode of execution 1,2 to replace the sky that is made of disc spring and move spring 60 and adopt the move schematic representation of example of spring 61 of the sky that is made of torsion spring.
In the structure of Figure 10, in the mode that connects Control Shaft 40 the sky spring 61 of moving is set at the sidepiece of swing arm 22.A move end of spring 61 of sky fastens with the projection 22a that is located at swing arm 22 sidepieces, and the move the other end of spring 61 of sky fastens with the buckling part 40a that is arranged on the Control Shaft 40.
And,, be applied with the power on the direction (direction that in Figure 10, is rotated counterclockwise) of withdrawing roll bearing surface 28 to swing arm 22 for swing arm 22 by the move active force of spring 61 of sky.Therefore according to the structure of Figure 10, the sky spring 61 of moving can play and the sky that is made of the disc spring identical effect of spring 60 of moving.That is, utilize the empty spring 61 of moving to make cam 54 and roller bearing surface 28 keep the state that carries out mechanical connection via cam abutment roller 48 and slide roller 50.
And in above-mentioned mode of execution 2, change the active force of secondary spring 64 according to distance apart from the worm gear 72 of the rotational position that is used to limit Control Shaft 40, thereby suppress the distortion of Control Shaft 40, but owing to the distortion of Control Shaft 40 is by valve spring 62, sky the producing with joint efforts on the Control Shaft sense of rotation that spring 60, secondary spring 64 produce of moving, if therefore can change and to make a concerted effort, then can suppress the distortion of Control Shaft 40 by the distance of each cylinder according to distance worm gear 72.That is, apart from worm gear 72 position far away more, by valve spring 62, sky move on the sense of rotation of the Control Shaft 40 that spring 60 and secondary spring 64 produce make a concerted effort more little, thereby can suppress distortion by the sense of rotation of the Control Shaft that active force produced 40 of spring.
Particularly, change the active force of the empty spring 60 of moving according to distance, thereby can suppress the distortion of Control Shaft 40 apart from the worm gear 72 of the rotational position that is used to limit Control Shaft 40.In this case, set the move active force of spring 60 of sky on the variable valve actuator for air 10 of each cylinder, make greatly more apart from the distance of worm gear 72, the move active force of spring 60 of sky is more little.As mentioned above, the active force of valve spring 62 and the empty spring 60 of moving acts on the Control Shaft 40 along same sense of rotation, and the amount of deformation of the Control Shaft 40 that the active force of valve spring 62 and the empty spring 60 of moving causes is along with become big away from worm gear 72.Therefore, the move active force of spring 60 of vast sky is more little more apart from the distance of worm gear 72 by making, and can suppress the distortion such as reverse on the Control Shaft 40.
And,, can suppress the distortion of Control Shaft 40 by change the active force of valve spring 62 according to distance apart from the worm gear 72 of the rotational position that is used to limit Control Shaft 40.In this case, set the active force of the valve spring 62 of each cylinder, so that more little apart from the distance of worm gear 72 active force big more, valve spring 62.The amount of deformation of the Control Shaft 40 that the active force of valve spring 62 and the empty spring 60 of moving causes is along with becoming big away from worm gear 72, therefore more little by making apart from the active force of the big more valve spring 62 of distance of worm gear 72, can suppress the distortion such as reverse on the Control Shaft 40.
In the time can changing sky and move the active force of spring 60, difference such as the line footpath by making each cylinder, the number of turn, coil diameter can change the move active force of spring 60 of each sky.And, on each cylinder, make the move decrement of spring 60 of sky differently constitute the sky assembly department of spring 60 of moving, thereby can change the move active force of spring 60 of each sky.And, as shown in figure 10, move under the situation of spring 61 constituting sky by torsion spring, change bearing of trend and the substantially horizontal angulation (representing with θ 1 among Figure 10) of buckling part 40a, can change the move active force of spring 61 of each sky by the spring 61 of moving according to each sky.Particularly, in Figure 10, the active force of spring 61 acts on the direction that swing arm 22 is rotated counterclockwise because each sky is moved, therefore, the length direction along Control Shaft 40 is big more away from worm gear 72 more for value by making angle θ 1, can make apart from the distance active force long more, that sky is moved spring 61 of worm gear 72 more little, the value representation of angle θ 1 and each sky position of the buckling part 40a that spring 61 fastens of moving wherein.So, under the situation of the variable position of buckling part 40a, needn't change the move designs of spring 61 of sky itself and can change the move active force of spring 61 of each sky.Thereby in each cylinder, when sky is moved the decrement of spring 60 when variable, or during the variable position of buckling part 40b, need not to prepare a plurality of skies that changed active force spring 60,61 of moving, thereby can reduce part number.And,, need not to carry out the operation from the different sky of active force is moved spring 60,61, selected etc. at move spring 60,61 o'clock of assembling sky.
And, when the active force of valve spring 62 is variable, also can be by making differences such as line footpath, the number of turn, coil diameter in each cylinder, and change the active force of each valve spring 62.And, as shown in figure 10, also can insert the valve spring sheet 63 that has nothing in common with each other according to each valve spring thickness by lower end to valve spring 62, change the active force of valve spring 62.In this case, long more apart from the distance of worm gear 72 along the length direction of Control Shaft 40, the thickness of valve spring sheet 63 is thin more, thereby can make apart from the distance active force long more, valve spring 62 of worm gear 72 more little.So, when changing the active force of valve spring 62, need not to change the active force that valve spring 62 designs own can change each valve spring 62 by valve spring sheet 63.Therefore, need not to prepare a plurality of valve spring 62 that changed active force, thereby can reduce part number.In addition, when assembling valve spring 62, need not to carry out the operation from the different valve spring 62 of active force, selected etc.
So, the sky active force of at least one of moving in spring 60, valve spring 62, the secondary spring is variable along the length direction of Control Shaft 40, at the long more position of the distance of distance worm gear 72, valve spring 62, sky move on the sense of rotation of the Control Shaft 40 that spring 60 and secondary spring 64 produce make a concerted effort more little, thereby can suppress the distortion of the sense of rotation of the Control Shaft 40 that the active force because of spring causes.
Mode of execution 3
Then, embodiments of the present invention 3 are described.The illustrated mode of execution 1 of the basic structure of the variable valve actuator for air 10 of mode of execution 3 and action thereof and Fig. 1～Fig. 4 is identical.
Figure 11 is the figure of the variable valve actuator for air 10 that is used to illustrate that embodiments of the present invention 3 relate to.Particularly, Figure 11 (A) is the planimetric map of expression variable valve actuator for air 10, and Figure 11 (B) is a profile from the B shown in Figure 11 (A) to view that represent this mechanism with.In addition, Figure 11 (C) cuts the major component of variable valve actuator for air open and the sectional view that obtains along the C-C cross section shown in Figure 11 (B).
Structure shown in Figure 11 comprises the cylinder head 80 of internal-combustion engine.Cylinder head 80 is by not shown Control Shaft bearing, and rotatably the retentive control axle 40.Though in Figure 11, omitted diagram, the structure of the major component of the variable valve actuator for air 10 that Fig. 1 and Fig. 2 are illustrated be arranged on cylinder head 80 near.The internal-combustion engine that present embodiment relates to also is provided with a plurality of cylinders (below be 4 cylinders) with in-line arrangement, and Control Shaft 40 is arranged to vertically block this four cylinders.
Be fixed with first gear 84 of flat dentation in the end of Control Shaft 40.Meshed second gear 86 that is similarly flat dentation on first gear 84.Center fixation at second gear 86 has running shaft 88.And, shown in Figure 11 (B), on running shaft 88, to be fixed with the worm gear 90 of semicircle shape with the overlapping mode of second gear 86.And running shaft 88 is remaining on the cylinder head 80 under the rotatable state.Adopt this structure, the relative rotation of second gear 86 of the worm gear 90 peaceful dentations of semicircle shape is kept definitely, be that running shaft is rotated with running shaft 88.
Dispose the motor 66 that is used to make Control Shaft 40 rotations as actuator in the side of cylinder head 80.On the running shaft of motor 66, be fixed with and above-mentioned worm gear 90 engaged worm 94.As shown in the figure, has spiral helicine gear grooved in the side of worm screw 94.On the other hand, on worm gear 90, form and gear grooved this spiral helicine gear grooved engagement, that tilt.
The direction of the running shaft 88 of the running shaft of motor 66 and worm gear 90 becomes 90 degree.Adopt worm screw 94 and worm gear 90, can not be subjected to the bias effect ground of this running shaft to give running shaft 88 the output transmission of torque of motor 92.And, adopt structure shown in Figure 11, the torque that is delivered to running shaft 88 can be delivered to Control Shaft 40 via first gear 86 and first gear 84.Therefore, adopt this structure, can control the rotation of Control Shaft 40 by the rotation of control motor 66.
And in the variable valve actuator for air of present embodiment, can in the angular range of regulation, adjust the rotational position of Control Shaft 40.Therefore, the gear mechanism that links to each other with Control Shaft 40 is so long as can make the device of Control Shaft 40 runnings get final product in this angular range.In the structure of present embodiment, this angular range can cover fully by making worm gear 90 Rotate 180 degree.Therefore in the present embodiment, as mentioned above, worm gear 90 can be made as the semicircle state, and dwindle the unwanted part that contains in the gear mechanism as far as possible.
And, shown in Figure 11 (C), the variable valve actuator for air of present embodiment, with the transmission of torque of motor 66 in the gear mechanism of Control Shaft 40, have secondary spring 96.Particularly, secondary spring 96 is made of the disc spring of the running shaft 88 that twines worm gear 90, and the one end is fixed on second gear 86, and the other end is fixed on the cylinder head 80.
Secondary spring 96 can produce assist torque around its central shaft.Adopt said structure, secondary spring 96 can be delivered to the rotating torques of prescribed direction second gear 86, running shaft 88 and worm screw 90.The rotation of running shaft 88 passes to Control Shaft 40, and the lift amount of intake valve is changed.And lift amount increases when rotating in one direction, and lift amount descends when rotating in the other direction.In the present embodiment, secondary spring 96 is arranged on the direction that lift amount increases and produces assist torque.
So, the variable valve actuator for air of present embodiment is that Control Shaft 40 is driven by motor 88 via the gear mechanism that contains worm gear 90 and worm screw 94.And, on this gear mechanism, be assembled with the secondary spring 96 that applies the assist torque of high-lift direction to Control Shaft 40, and this assist torque directly imposes on worm gear 90.
By the combination of worm gear 90 and worm screw 94, can realize higher forward efficiency and lower negative efficient.Therefore, adopt the variable valve actuator for air of present embodiment, the torque and high-efficient ground that motor 66 is produced is delivered to Control Shaft 40, on the other hand, can stop the transmission of torque that is input to Control Shaft 40 to arrive motor 66.Therefore, adopt this variable valve actuator for air,, can accurately control the rotational position of Control Shaft 40 by control motor 66.
And, in the variable valve actuator for air of present embodiment, can relax by above-mentioned assist torque and make the influence of Control Shaft 40 to the external force of little lift direction rotation, can relax the influence of the active force of the reaction force of valve spring 62 and the empty spring 60 of moving.When not having this assist torque, make Control Shaft 40 when the high-lift direction is rotated, for the frictional force of revolting various machineries and the reaction force of valve spring 62 etc., need to produce this rotation.In this case, require motor 66 to produce bigger torque, it drives needs a large amount of electric power, and is easy to produce the problem of reversing on generation gear mechanism and the Control Shaft 40.
On the contrary, if can relax the influence of the reaction force etc. of valve spring 62 by assist torque, then available less motor torque makes Control Shaft 40 rotate to the high-lift direction.Therefore, adopt the variable valve actuator for air of present embodiment, compare when not having secondary spring 96, can obtain following advantage: the minimizing of the torsional capacity of the minimizing of the power consumption that the miniaturization of motor 66, drive controlling axle 40 are required, Control Shaft 40 etc. etc.
And then, adopt the structure of present embodiment, because assist torque is directly imposed on worm gear 90, therefore can make static Control Shaft 40 successfully begin rotation.Below, with reference to Figure 12 its reason is described.Figure 12 is the forward efficiency (from the transmission efficiency of worm screw 94 to the torque of worm gear 96) of the gear mechanism that combined by worm screw 94 and worm gear 90 of expression and the figure of the relation between the transient speed.Particularly, the represented curve representation of single-point among Figure 12 line is the forward efficiency when worm gear 90 applies assist torque not, the forward efficiency of the curve representation shown in the solid line among Figure 12 when worm gear 90 applies the assist torque of direction of auxiliary rotation.
Compare with the static friction coefficient of flat between cog, the static friction coefficient between worm screw 94 and the worm gear 90 is enough big value.And, when the masterpiece of little lift direction is used for Control Shaft 40, if the torque that motor 66 produces to the high-lift direction then between worm screw 94 and worm gear 90, produces bigger load when it is overlapped.Therefore, when not having assist torque, between worm screw 94 and worm gear 90, produce bigger stiction.Consequently, shown in the line of the single-point among Figure 12, in approaching zero the zone of transient speed, forward efficiency obviously becomes lower value.And when influence big when the transient speed change, static friction coefficient disappeared, its forward efficiency became higher value and keeps stablizing.
When the assist torque of high-lift direction acts on worm gear 90, can offset the power of the little lift direction that input to Control Shaft 40 by this assist torque, consequently, the load when acting on static between worm screw 94 and the worm gear 90 can be less value.When this load during for less value, the stiction that produces between worm screw 94 and the worm gear 90 also becomes less value, and shown in the solid line among Figure 12, transient speed obviously improves at the forward efficiency of lower region.And, when when this regional forward efficiency improves, the action of Control Shaft 40 when the high-lift direction is rotated become smoothly, can improve its control accuracy.
As mentioned above, adopt the variable valve actuator for air of present embodiment, under the effect of secondary spring 96, Control Shaft 40 is successfully rotated to the high-lift direction.And the external force of little lift direction acts on Control Shaft 40 originally, therefore making Control Shaft 40 when little lift direction moves, must realize good acting characteristic.Therefore, adopt the variable valve actuator for air of present embodiment, can make Control Shaft 40 rotation smoothly on either direction with less power.
Though in above-mentioned mode of execution 3,, utilize the working angle of change air door body 12 and the mechanism of lift amount by making Control Shaft 40 rotations, secondary spring 96 is assembled in the gear mechanism that produces this rotation, the present invention is not limited to this.That is, also can move vertically, utilize the working angle of change air door body 12 and the mechanism of lift amount, will be assembled in the gear mechanism of Control Shaft 40 transmission of drive force to the secondary spring of high-lift direction generation assist torque by making Control Shaft 40.
And identical with mode of execution 1, in above-mentioned mode of execution 3, the sky spring 60 of moving is the same with valve spring 62, produces the active force that variable valve actuator for air 10 is changed to little lift direction, and the invention is not restricted to this.That is, the present invention also is effective for the sky mechanism that spring produces to the active force of high-lift direction of moving.
In above-mentioned mode of execution 3, variable valve actuator for air 10 changes working angle and lift amount simultaneously according to the rotational position of Control Shaft 40, and the invention is not restricted to this.That is, variable valve actuator for air also can only change in working angle and the lift amount one.In this case, for producing to big effect angular direction to the power of the Control Shaft application of force of the working angle that only changes air door body or produce to the high-lift direction power of the Control Shaft application of force of the lift amount that only changes air door body is provided with secondary spring, thereby can obtain the effect identical with present embodiment.
In above-mentioned mode of execution 3, the first arm parts 24 and second arm member 26 are equivalent to " changeable mechanism " in above-mentioned the 7th invention, motor 66 is equivalent to " actuator " in above-mentioned the 7th invention, worm screw 94, worm gear 90, second gear 86 and first gear 84 are equivalent to " gear mechanism " in above-mentioned the 7th invention, and secondary spring 96 is equivalent to " the auxiliary force generating means " in above-mentioned the 7th invention.
In addition, identical with mode of execution 2, in mode of execution 3, the move active force of spring 60 or valve spring 62 of sky is variable on the length direction of Control Shaft 40, the long more position of distance apart from first gear 84, making a concerted effort of the sense of rotation of the Control Shaft 40 that valve spring 62 and the empty spring 60 of moving produce is more little, thus the distortion of the sense of rotation of the Control Shaft 40 that can suppress to cause by the active force of these springs.For example, apart from the long more position of distance of first gear 84, the move active force of spring 60 of sky is more little, thereby can suppress reversing of Control Shaft.
Mode of execution 4
Then embodiments of the present invention 4 are described with reference to Figure 13.Figure 13 is the figure of lubricating oil flow path that is used to illustrate the variable valve actuator for air of embodiments of the present invention 3.Particularly, Figure 13 (B) is the sectional view that amplifies the periphery of the mate of representing worm screw 94 and worm gear 90.And Figure 13 (A) cuts the variable valve actuator for air in the present embodiment open resulting sectional view along the A-A view of Figure 13 (B).In addition, configuration up and down shown in Figure 13, the relationship consistency of being realized during with on-vehicle internal combustion engine.
The variable valve actuator for air of present embodiment except lubricating oil flow path with following explanation, in fact other all the variable valve actuator for air with mode of execution 3 is identical.Promptly, in Figure 13 (A) and Figure 13 (B), for convenience worm gear 90 is made as the full circle shape, and worm gear 90 directly is fixed on the Control Shaft 40, and this some be not the essential part of invention, and the mechanism of mode of execution 4 is characterised in that the lubricating oil flow path of following explanation.In Figure 13,, and omit or simplify its explanation for reference character identical with the composed component of above explanation or that the corresponding elements mark is identical.
Shown in Figure 13 (B), in the variable valve actuator for air of present embodiment, motor 66 is fixed on the cylinder head 80.The inner space of cylinder head 80 is assembled into cylinder head cover 100 sealings on it.Form space 102, and the space 104 of the profile of imitation worm gear 90 of the profile of imitation worm screw 94 in the inside of cylinder head cover 100.These spaces 102,104 form one mutually, wherein contain worm screw 94 and worm gear 90 compactly.
Space 104 being used for accommodating worm gear 90 is communicated with fuel feeding path 106 at an upper portion thereof.Fuel feeding path 106 is the paths that will be directed to by a part of lubricant oil of oil pump force feed in the internal combustion engine operation process in space 102 and 104.On the running shaft of motor 66, install and twine its oil seal washer 108, that space 102 and space outerpace are cut off on every side.And, shown in Figure 13 (A), install on the Control Shaft 104 and surround its oil seal washer 110, that space 102,104 and space outerpace are cut off on every side.Therefore, in the operation process of internal-combustion engine, space 102 and 104 inside are full of lubricant oil.
Shown in Figure 13 (A), be formed on the oil circuit 112 that extends on the axle direction in the inside of Control Shaft 40.Sealed plug 114 sealings in the end of oil circuit 112.And Control Shaft 40 is provided with the oil supply hole 116 that space 102,104 is communicated with oil circuit 92.Therefore, in the internal combustion engine operation process, the lubricant oil that is full of in the space 102,104 supplies to oil circuit 112 by oil supply hole 116.
Cylinder head 80 has the bearing 118 that is used for retentive control axle 40 in the both sides of each cylinder of internal-combustion engine.Control Shaft 40 is kept by this bearing 118 and can rotate.And the major component of variable valve actuator for air 10 that will be corresponding with each cylinder on by the position of two bearing 118 clampings is assembled on the Control Shaft 40.That is, on the position by above-mentioned two bearing 118 clampings, two swing arms 22 and a non-swing part 36 that variable valve actuator for air 10 is had are assembled on the Control Shaft 40.
On Control Shaft 40, on the position corresponding, has oil supply hole 120 to oil circuit 112 openings with the non-swing part of each bearing 118, each swing arm 22 and each 36.And, on non-swing part 36, being provided with oil circuit 122, the one end is to these oil supply hole 120 openings, and the other end is to the side opening of the running shaft 46 of oscillating roller portion 38.Therefore, the lubricant oil at the internal circulation of Control Shaft 40 supplies to each lubricating point by oil supply hole 120, oil circuit 122 etc.
In the variable valve actuator for air of present embodiment, 102,104 lubricant oil that flow out to the oil circuit 112 of Control Shaft 40 via each lubricating point etc., are reclaimed by the oil storage tank of internal combustion engines afterwards from the space.And when internal-combustion engine stops and stopping from fuel feeding path 106 when new lubricant oil is supplied with in space 102,104, lubricant oil no longer flow into oil circuit 112 soon, the loop ends of lubricant oil.
And in the stream of lubricant oil shown in Figure 13, the lubricant oil that flow into space 102,104 only flow into the outside that oil circuit 112 promptly flows out to space 102,104 by oil supply hole 116.And this oil supply hole 116 is arranged on the position of the mate that is higher than worm screw 94 and worm gear 90.Therefore, the pasta of the lubricant oil in the space 102,104 when internal-combustion engine stops, also can maintaining on the position of the mate that is higher than worm screw 94 and worm gear 90.
Under these conditions, can lubricant oil be supplied between worm screw 94 and the worm gear 90 remaining moisteningly.Therefore, adopt the variable valve actuator for air of present embodiment, even just started the back at internal-combustion engine, lubricant oil does not fully carry out under the circuit situation as yet, also can with the output torque and high-efficient of motor 66 pass to Control Shaft 40.
As mentioned above, variable valve gear involved in the present invention can reduce the driving load of the Control Shaft of the lift amount that is used to change air door body and working angle, can be used for being located in the multiple variable valve gear on the internal-combustion engine.
Claims (11)
1. variable valve actuator for air changes the lift amount and the working angle of the air door body of internal-combustion engine, it is characterized in that having:
First cam of rotation along with the crank rotation;
Transferring elements has second cam, and the rotation of this second cam and described first cam is swung synchronously, and the force transmission that described first cam is produced arrives described air door body;
Be adjusted to the Control Shaft of the rotational position of regulation;
Changeable mechanism changes the hunting range of described transferring elements according to the rotational position of described Control Shaft, and changes the lift amount and the working angle of described air door body;
The sky spring of moving makes described transferring elements to the described first cam application of force, to keep being connected of described transferring elements and described first cam; And
Secondary spring, revolt described sky move spring active force and to the described transferring elements application of force.
2. variable valve actuator for air as claimed in claim 1 is characterized in that,
Described sky is moved direction that spring changes from high-lift amount, the big little lift amount of working angle one side direction, little working angle one side to the lift amount of described air door body and working angle to the described transferring elements application of force,
The lift amount of described air door body and working angle are the closer to little lift amount, little working angle one side, and the active force that acts on the described secondary spring on the described transferring elements is big more.
3. variable valve actuator for air as claimed in claim 1 or 2 is characterized in that,
Have and make the valve spring of described air door body to the described transferring elements application of force,
Described secondary spring is revolted the active force that acts on the described valve spring on the described transferring elements via described air door body, to the described transferring elements application of force.
4. variable valve actuator for air as claimed in claim 3 is characterized in that,
Have: the actuator that produces the driving force of the rotational position be used to change described Control Shaft; With
Gear mechanism between described actuator and described Control Shaft;
Link to each other with shared described Control Shaft with a plurality of described transferring elements of the corresponding setting of described air door body of each cylinder;
Described sky is moved the active force of spring, described secondary spring and described valve spring via the sense of rotation transmission to described Control Shaft of described transferring elements and described changeable mechanism;
On the length direction of described Control Shaft, more away from described gear mechanism, described sky move the active force of spring, described secondary spring and described valve spring be applied to power on the sense of rotation of described Control Shaft make a concerted effort more little.
5. variable valve actuator for air as claimed in claim 4 is characterized in that, and is on the length direction of described Control Shaft, more away from described gear mechanism, big more to the active force of the described secondary spring of the described transferring elements application of force.
6. variable valve actuator for air as claimed in claim 4 is characterized in that, and is on the length direction of described Control Shaft, more away from described gear mechanism, more little to the move active force of spring of the described sky of the described transferring elements application of force.
7. a variable valve actuator for air has the working angle of the air door body that changes internal-combustion engine and/or the function of lift amount, it is characterized in that having:
Control Shaft, for a change described working angle and/or lift amount and its state is controlled;
Swing arm between cam and air door body, and is swung synchronously with the rotation of cam, thereby this action of cam power is delivered on the described air door body;
Changeable mechanism changes the basic relative angle of described swing arm with respect to described air door body according to the state of described Control Shaft;
Actuator produces the driving force of the state be used to change described Control Shaft;
Gear mechanism is between described actuator and described Control Shaft; And
The auxiliary force generating means applies the auxiliary force that makes on the direction that working angle and/or lift amount increase to described gear mechanism.
8. variable valve actuator for air as claimed in claim 7 is characterized in that,
Described gear mechanism comprises interconnected worm and worm wheel, and wherein worm screw is positioned at described actuator one side, and worm gear is positioned at described Control Shaft one side;
Described auxiliary force is applied to described worm gear or forms on the structure of one with described worm gear.
9. as claim 7 or 8 described variable valve actuator for air, it is characterized in that,
Have the sky spring of moving, make described swing arm to the described cam application of force, keeping the mechanical connection of described swing arm and described gear,
Require more to produce bigger working angle and/or lift amount, direction that the amount of deformation of spring increases moves to described sky is moved more in described swing arm.
10. variable valve actuator for air as claimed in claim 9 is characterized in that,
Link to each other with shared described Control Shaft with a plurality of described swing arm of the corresponding setting of described air door body of each cylinder;
On the length direction of described Control Shaft, more away from described gear mechanism, the move active force of spring of described sky is more little.
11. a variable valve actuator for air, the lift amount and the working angle of the air door body of change internal-combustion engine is characterized in that having:
First cam of rotation along with the crank rotation;
Transferring elements has second cam, and the rotation of this second cam and described first cam is swung synchronously, and the force transmission that described first cam is produced arrives described air door body;
Be adjusted to the Control Shaft of the rotational position of regulation;
Changeable mechanism changes the hunting range of described transferring elements according to the rotational position of described Control Shaft, and changes the lift amount and the working angle of described air door body;
The sky spring of moving makes described transferring elements to the described first cam application of force, to keep being connected of described transferring elements and described first cam; And
Secondary spring produces and the move active force of active force antagonism of spring of described sky.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003420514 | 2003-12-18 | ||
| JP420514/2003 | 2003-12-18 | ||
| JP043093/2004 | 2004-02-19 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101971313A Division CN101178019A (en) | 2003-12-18 | 2004-12-07 | Variable valve mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1914408A true CN1914408A (en) | 2007-02-14 |
| CN100417787C CN100417787C (en) | 2008-09-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800373088A Expired - Fee Related CN100417787C (en) | 2003-12-18 | 2004-12-07 | Variable valve mechanism |
| CNA2007101971313A Pending CN101178019A (en) | 2003-12-18 | 2004-12-07 | Variable valve mechanism |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101971313A Pending CN101178019A (en) | 2003-12-18 | 2004-12-07 | Variable valve mechanism |
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| Country | Link |
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| CN (2) | CN100417787C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101457677B (en) * | 2008-12-31 | 2010-09-08 | 奇瑞汽车股份有限公司 | Valve variable valve mechanism |
| CN101457673B (en) * | 2007-12-14 | 2012-10-03 | 现代自动车株式会社 | Variable ventilhubvorrichtung |
| CN103670579A (en) * | 2013-11-29 | 2014-03-26 | 长城汽车股份有限公司 | Mechanism for continuously adjusting engine valve lift |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2019229490A1 (en) | 2018-05-30 | 2019-12-05 | Carrier Corporation | Energy management systems (ems) for transportation refrigeration units (tru) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3167180B2 (en) * | 1992-07-03 | 2001-05-21 | マツダ株式会社 | Engine valve timing control device |
| JPH07293216A (en) * | 1994-04-26 | 1995-11-07 | Mitsubishi Automob Eng Co Ltd | Valve system of internal combustion engine |
| JPH08246824A (en) * | 1995-03-04 | 1996-09-24 | Minoru Nakagawa | Reciprocating contact sliding opening/closing and continuously variable valve timing device |
| TW387033B (en) * | 1997-06-24 | 2000-04-11 | Honda Motor Co Ltd | Valve operating system in internal combustion engine |
-
2004
- 2004-12-07 CN CNB2004800373088A patent/CN100417787C/en not_active Expired - Fee Related
- 2004-12-07 CN CNA2007101971313A patent/CN101178019A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101457673B (en) * | 2007-12-14 | 2012-10-03 | 现代自动车株式会社 | Variable ventilhubvorrichtung |
| CN101457677B (en) * | 2008-12-31 | 2010-09-08 | 奇瑞汽车股份有限公司 | Valve variable valve mechanism |
| CN103670579A (en) * | 2013-11-29 | 2014-03-26 | 长城汽车股份有限公司 | Mechanism for continuously adjusting engine valve lift |
| CN103670579B (en) * | 2013-11-29 | 2016-01-20 | 长城汽车股份有限公司 | A kind of engine air valve lift continuous setup mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101178019A (en) | 2008-05-14 |
| CN100417787C (en) | 2008-09-10 |
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