CN105422205B - The valve mechanism of engine - Google Patents
The valve mechanism of engine Download PDFInfo
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- CN105422205B CN105422205B CN201510594564.7A CN201510594564A CN105422205B CN 105422205 B CN105422205 B CN 105422205B CN 201510594564 A CN201510594564 A CN 201510594564A CN 105422205 B CN105422205 B CN 105422205B
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- cam shaft
- admission cam
- exhaust cam
- admission
- exhaust
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Abstract
A kind of valve mechanism of engine, including：The intake valve and air bleeding valve of engine；Camshaft, the camshaft are provided with admission cam and exhaust cam, and admission cam and exhaust cam are rotated by the bent axle of engine, so as to open and close intake valve and air bleeding valve respectively；And phase variable mechanism, the phase variable mechanism make the phase of the direction of rotation of admission cam or exhaust cam change relative to bent axle.Camshaft includes：Admission cam shaft, admission cam shaft are provided with admission cam；And exhaust cam shaft, exhaust cam shaft is provided with exhaust cam, and admission cam shaft and exhaust cam shaft are configured to relative displacement in a rotational direction；And wherein, phase variable mechanism includes：Driven member, is rotated by bent axle；Guiding elements, guiding elements rotate together with admission cam shaft or exhaust cam shaft, and can be relative to driven member relative displacement on direction of rotation and axis direction；Governor weight, governor weight are arranged between driven member and guiding elements；And pushing member, pushing member pushes up driven member and guiding elements making driven member and guiding elements side close to each other, and since the motive force of centrifugal force resistance pushing member causes governor weight to move, thus relative to driven member on direction of rotation and axis direction relative displacement occurs for guiding elements, so that phase changes relative to bent axle in a rotational direction for admission cam or exhaust cam.
Description
Technical field
The present invention relates to a kind of valve mechanism of the engine of Single Over Head Camshaft (SOHC) type, the valve mechanism of the engine
Including phase variable mechanism, which is used to make the phase of the direction of rotation of admission cam or exhaust cam opposite
Change in bent axle, so as to change the valve timing of inlet valve and exhaust valve.
Background technology
In recent years, there is provided include the valve mechanism of valve timing variset, which is used for basis and draws
Mode of operation held up etc. changes the valve timing of inlet valve and exhaust valve, such as (Japan Patent is opened flat No.2013- in patent document 1
7293) disclosed with patent document 2 (Japan Patent is opened flat No.2010-31855).
The valve mechanism of engine described in patent document 1 and 2 each includes camshaft phase changeable mechanism, should
Camshaft phase changeable mechanism is used to make the phase of the direction of rotation of camshaft change relative to bent axle, so as to change
The inlet valve of engine and the valve timing of exhaust valve.
However, regrettably, the camshaft phase change mechanism described in above-mentioned prior art document is applied to Double Tops
The valve mechanism of camshaft (DOHC) type is put, wherein, a camshaft includes admission cam and another camshaft includes
Exhaust cam, and therefore, this DOHC types are not suitable for the valve mechanism of SOHC types.
The content of the invention
The present invention take into account said circumstances, and the object of the present invention is to provide a kind of valve mechanism of engine, even if
In the valve mechanism of SOHC types, which can improve performance so as to stablize during the change of valve timing, and
Obtain the improved response for change.
Above and other purposes can be according to the present invention by setting the valve mechanism of engine to realize, the valve machine of the engine
Structure includes：The intake valve and air bleeding valve of engine；Camshaft, the camshaft are provided with admission cam and exhaust cam, admission cam
Rotated with exhaust cam by the bent axle of engine, so as to open and close intake valve and air bleeding valve respectively；And phase variable mechanism,
The phase variable mechanism makes the phase of the direction of rotation of admission cam or exhaust cam change relative to bent axle；Engine
Valve mechanism is characterized in that camshaft includes：Admission cam shaft, admission cam shaft are provided with admission cam；And exhaust cam
Axis, exhaust cam shaft is provided with exhaust cam, and admission cam shaft and exhaust cam shaft are configured in direction of rotation
Upper relative displacement；And wherein, phase variable mechanism includes：Driven member, driven member be fixed on exhaust cam shaft or into
Rotated on gas camshaft and by bent axle；Guiding elements, guiding elements are configured to and admission cam shaft or exhaust cam shaft one
Rotation is played, and can be relative to driven member relative displacement on direction of rotation and axis direction；Governor weight, governor weight are set
Put between driven member and guiding elements；And pushing member, pushing member are configured to make driven member and guiding elements
Side close to each other pushes up driven member and guiding elements, and since the motive force of centrifugal force resistance pushing member causes
Governor weight moves, and thus relative to driven member on direction of rotation and axis direction relative displacement occurs for guiding elements, from
And make admission cam or exhaust cam phase changes relative to bent axle in a rotational direction.
Aforementioned aspect of the present invention it is preferred in, following theme feature can be used.
It is desirable that, exhaust cam shaft is coaxially disposed in the outside of a part for admission cam shaft.
It is desirable that, it is provided with admission cam, exhaust cam and phase variable mechanism in sequence on camshaft.
It is desirable that, one in admission cam shaft and exhaust cam shaft is provided with stop pin, and another formed with
For locking the latch recess of stop pin；Wherein, latch recess is sized to allow for admission cam shaft and exhaust cam shaft
The relative displacement in prescribed limit in a rotational direction.
It is further desirable that admission cam shaft is formed with oily groove, and to be arranged on exhaust convex for the exhaust outlet of oily groove
The slidingsurface with admission cam shaft sliding contact of wheel shaft.
According to the present invention of feature as described above, due to the motive force of centrifugal force resistance pushing member cause be arranged on it is driven
Governor weight movement between component and guiding elements, and therefore, guiding elements can be relative to driven member in rotation side
To with axis direction top offset so that the phase on the direction of rotation of admission cam or exhaust cam occurs relative to bent axle
Opposite change.Therefore, even in the valve mechanism for the SOHC types for being provided with the camshaft including admission cam and exhaust cam
In, it can reliably change valve timing using simple structure, therefore allow the operating characteristics during valve timing is changed to be steady
Fixed, therefore improve the reliability of valve mechanism and improve the response performance changed.
Brief description of the drawings
In attached drawing：
Fig. 1 is along the direction of the axis perpendicular to camshaft, is drawn using the SOHC types of one embodiment of the present of invention
The sectional view for the valve mechanism held up, and cylinder cover of display engine etc. together.
Fig. 2 is the stereogram of the valve mechanism of the engine of explanatory drawin 1, and Fig. 2 includes intake valve, air bleeding valve and rocking arm, even
Steaming cylinder cap etc.；
Fig. 3 is the plan of a part and the cylinder cover of the valve mechanism for showing Fig. 2 etc.；
Sectional views of the Fig. 4 along the line IV-IV in Fig. 3；
Sectional views of the Fig. 5 along the line V-V in Fig. 3；
Fig. 6 is the stereogram for showing camshaft and phase variable mechanism shown in Fig. 2 to Fig. 4；
Fig. 7 is the exploded perspective view of the camshaft and phase variable mechanism that show Fig. 6；
Fig. 8 is the decomposition side view of the camshaft and phase variable mechanism that show Fig. 6；
Fig. 9 is the side view of the camshaft and phase variable mechanism that show Fig. 6；
Figure 10 is the sectional view along the line X-X in Fig. 9；
Figure 11 is the schematic sectional view along the line XI-XI in Fig. 9, it is shown that the exhaust cam shaft shown in Fig. 9 and 10
Latch recess and admission cam shaft stop pin between position relationship；
Figure 12 A and 12B show the exhaust cam shaft and driven member of the phase variable mechanism in Fig. 9 and 10, wherein Figure 12 A
It is the stereogram for showing exhaust cam shaft, and Figure 12 B are the front views for showing driven member；
Figure 13 A are shown in the front view of the driven member in Fig. 9 and 10, and Figure 13 B are that XIII is shown in Figure 13 A
Partial partial enlarged view；
Figure 14 A show the front view of the guiding elements of Fig. 9 and 10, and Figure 14 B are along the XIV-XIV lines in Figure 14 A
Sectional view, and Figure 14 C are the partial enlarged views of Figure 14 B；
Figure 15 A to 15C are the schematic diagrames for illustrating operating position, each is shown in the range of low engine revolution in Fig. 9
With 10 in phase variable mechanism in governor weight position；With
Figure 16 A to 16C are the schematic diagrames for illustrating operating position, each is shown in the range of high engine revolutions in Fig. 9
With 10 in phase variable mechanism in governor weight position.
Embodiment
Hereinafter, the embodiment of the present invention will be described with reference to the drawings.It is further noted that herein by shown in refer to the attached drawing
State uses the term of " upper and lower ", " left and right " etc. display direction.
As described above, Fig. 1 is along the direction of the axis perpendicular to camshaft, using drawing for one embodiment of the present of invention
The sectional view of the valve mechanism for the SOHC types held up, and cylinder cover etc. is shown together.In addition, Fig. 2 is the valve for showing Fig. 1
The stereogram of mechanism, and Fig. 3 is the plan of a part for the valve mechanism for showing Fig. 2.
With reference to figure 1, four-cycle, single-cylinder engine 10 is provided with single overhead cam in the cylinder cover 11 for being attached to cylinder block 1
The valve mechanism 12 of axis (SOHC) type (system).Valve mechanism 12 is included for example, intake valve 13 and air bleeding valve 14, be provided with into
The camshaft 17 of gas cam 15 and exhaust cam 16, intake rocker 18 and exhaust rocker arm 19, and phase variable mechanism 44, below will
These are described with reference to figure 2 and 3.
Camshaft 17 includes phase variable unit 44, which, which has, is provided with as shown in Figures 2 and 3 convex
Take turns the driven member 45 of driven sprocket 20.20 power of cam driven sprocket wheel is dynamically connected to by not illustrated cam chain in figure
Not illustrated (with reference to figure 1) actuated by cams sprocket wheel being formed in bent axle 5 in figure.Therefore, the rotation of bent axle 5 passes through cam chain quilt
Camshaft 17 is transferred to rotate camshaft 17.Camshaft 17 is provided with admission cam 15 and exhaust cam 16, admission cam 15
With exhaust cam 16 by for example so that exhaust cam 16 be positioned close to 20 side of cam driven sprocket wheel in a manner of in axis direction
Upper configured in parallel.
Here, formed with cylinder-bore 3, piston 2 is slidably reciprocal in cylinder-bore 3 to be transported shown cylinder block 1 in Fig. 1
It is dynamic.The connecting rod 4 that reciprocates through of piston 2 is transferred to bent axle 5 to be converted into rotation.
Intake rocker 18 and exhaust rocker arm 19 are swingably supported by rocker shaft 24 respectively, and each of these arms is set
Put the other end with adjusting screw 23 in the one end of rocker shaft 24 with roller 22 and rocker shaft 24.Intake rocker 18 is arranged to
It is enough to be rolled by making roller 22 be contacted with admission cam 15, and adjusting screw 23 is contacted with intake valve 13.Similarly, meanwhile,
Exhaust rocker arm 19 is arranged to roll by making roller 22 contact with exhaust cam 16, and adjusting screw 23 and air bleeding valve 14
Contact.
Therefore, when admission cam 15 and exhaust cam 16 are rotated according to the rotation of camshaft 17, intake rocker 18
Roller 22 is rolled along the cam contour of admission cam 15, to allow intake rocker 18 to swing, therefore passes through the tune of intake rocker 18
Whole 23 opened/closed intake valve 13 of screw.Meanwhile the roller 22 of exhaust rocker arm 19 is rolled along the cam contour of exhaust cam 16,
To allow exhaust rocker arm 19 to swing, therefore the 23 opened/closed air bleeding valve 14 of adjusting screw for passing through exhaust rocker arm 19.
In Fig. 1, reference numeral 25 and 26 indicates adjusting nut and valve spring respectively.Further, reference numeral 21 indicates
The bar guiding of cylinder cover 11 is attached to, to guide the movement of each bar of intake valve 13 and air bleeding valve 14.
As shown in figure 4, in the camshaft 17 for the valve mechanism 12 being configured as above, the first ball bearing 27 is installed on exhaust
On camshaft 32, and the second ball bearing 28 is also mounted on admission cam shaft 31.First ball bearing 27 and the second ball bearing 28
It is maintained in camshaft case 29, so that camshaft 17 is pivotably supported, the upper part of camshaft case 29 and cylinder cover 11
It is integrally formed.
As shown in figs. 4 and 6, being provided with the camshaft 17 of admission cam 15 and exhaust cam 16 includes admission cam shaft 31,
Admission cam shaft 31 is integrally arranged with admission cam 15, and as shown in FIG. 7 and 8, exhaust cam shaft 32 and exhaust cam 16
It is integrally arranged, as shown in FIG. 7 and 8.
In addition, as shown in Figures 9 and 10, the axle portion 31A insertion exhaust cam shafts 32 of admission cam shaft 31, so as to will be vented convex
Wheel shaft 32 is coaxially disposed in the outside of axle portion 31A.By this way, admission cam shaft 31 and exhaust cam shaft 32 are constructed
Into relative displacement in a rotational direction.
The relative displacement of admission cam shaft 31 and exhaust cam shaft 32 position in a rotational direction is only in prescribed limit
Inside it is allowed to.That is, such as Fig. 6 and 9, in admission cam shaft 31, axle portion 31A and diameter are more than axle portion 31A and are provided with air inlet
The cam forming portion 31B of cam 15 is moulded integrally to each other.The cam forming portion 31B of admission cam shaft 31 be provided with parallel into
The axes O of gas camshaft 31, the stop pin 33 protruded towards axle portion 31A.In addition, in exhaust cam shaft 32, exhaust cam 16
Formed with the latch recess 34 to its side surface, latch recess 34 is used for what is assembled in admission cam shaft 31 and exhaust cam shaft 32
Stop pin 33 is locked under state.
As shown in figure 11, when the admission cam shaft 31 being co-axially arranged in exhaust cam shaft 32 is convex relative to being vented
When wheel shaft 32 relatively moves in a rotational direction, the stop pin 33 of admission cam shaft 31 and the latch recess of exhaust cam shaft 32
34 both ends of the surface 35 contact, therefore adjust the opposite position of admission cam shaft 31 in a rotational direction relative to exhaust cam shaft 32
Move.Therefore, the size between two opposing end surfaces 35 of latch recess 34 is set to admission cam shaft 31 relative to exhaust cam
Relative displacement allows in the prescribed limit of angle δ axis 32 in a rotational direction.
Meanwhile as shown in Figures 3 and 5, multiple bolt-inserting holes 36, such as four holes, are formed in camshaft case 29, from
And run through camshaft case 29 and cylinder cover 11.When not illustrated head fastening bolt is inserted into bolt-inserting hole 36 respectively in figure
When, the cylinder cover 11 Unitarily molded with camshaft case 29 is fastened and fixed to crankcase together with cylinder block 1.
As shown in Figures 4 and 5, camshaft case 29 is formed with the oil feeding groove connected with least one bolt-inserting hole 36
37.In addition, as shown in figures 4 and 10, admission cam shaft 31 is formed with main oily groove 38 and secondary oily groove 39,38 edge of main oil groove
Axes O extension, secondary oil groove 39 connects and in the extension in the radial direction of admission cam shaft 31 with main oily groove 38.Main oil
Groove 38 is connected with oil feeding groove 37.Further, the exhaust outlet 40 of secondary oily groove 39 is with the axle portion 31A's of admission cam shaft 31
Outer surface connects, i.e. annular groove 42 is formed in the slidingsurface 41 contacted with exhaust cam shaft 32.
Therefore, the lubricating oil for bolt-inserting hole 36 being risen through on the direction of arrow Q (with reference to figure 5) passes through camshaft casing
The oil feeding groove 37 of body 29 is fed to the main oily groove 38 of admission cam shaft 31, and also recessed from the pair oil of admission cam shaft 31
Groove 39 is supplied into annular groove 42, so as to lubricate the admission cam shaft 31 and exhaust cam shaft 32 that can be relatively rotated.
As shown in Fig. 4,6,9 and 10, camshaft 17 has been continuously provided admission cam 15, exhaust cam 16 and phase variable
Mechanism 44.Phase variable mechanism 44 act as changing admission cam 15 or exhaust cam 16 (in the present embodiment relative to bent axle 5
In be admission cam 15) phase in a rotational direction, and phase variable mechanism include driven member 45, guiding elements 46,
Governor weight 47, pushing member 48 and circlip 49.
In the present embodiment, exhaust cam 16 is driven in rotation with bent axle 5 with identical phase in a rotational direction, so that
Open and/or close air bleeding valve 14.In contrast, admission cam 15 is in a rotational direction with identical or different from bent axle 5
Phase is by 44 rotation driving of phase variable mechanism, so as to open and/or close intake valve 13.Phase variable mechanism 44 is according to engine
The valve timing of 10 mode of operation control intake valve 13, so as to adjust the opening for opening timing and air bleeding valve 14 of intake valve 13
The overlap condition of timing.
For example, phase variable mechanism 44 is set, and in the high engine speed range of engine 10, the valve of intake valve 13 and air bleeding valve 14
Overlapping is small, so as to prevent inlet air to be blown, and therefore, improves output and fuel consumption and reduces in exhaust
Harmful substance.In addition, phase variable mechanism 44 is also set, and in the low engine speed range of engine 10, intake valve 13 and air bleeding valve 14
Valve lap be big so that by using air inlet inertia improve intake efficiency, to improve the moment of torsion of engine 10.
As shown in Figure 10 and 13, driven member 45 is provided with cam driven sprocket wheel 20 in its outer surface, and by passing through
The rotation driving of the bent axle 5 of cam chain transmission, so as to be provided in a rotational direction relative to bent axle lasting (or identical
) phase.
In addition, also shown in FIG. 12, driven member 45 is provided with adaptation groove 53 in its inner peripheral surface, and is vented convex
Wheel shaft 32 is provided with adaptation protuberance 54 in its one end.Adaptation groove 53 and adaptation protuberance 54 fit each other, driven to allow
Component 45 is fixed to exhaust cam shaft 32.
As shown in Fig. 4,7 and 8, guiding elements 46 is arranged to integrally revolve with admission cam shaft 31 by engaging axis 55
Turn.That is, the axle portion 31A of admission cam shaft 31 is formed with the through hole 56 for running through axle portion 31A in radial directions along its axes O.
In addition, engagement axis 55 is provided with projection 57 in its opposite end, and it is inserted into the through hole 56 of admission cam shaft 31.Inserting
Enter in state, two projections 57 for engaging axis 55 protrude (protrusion) from the axle portion 31A of admission cam shaft 31.Projection 57 respectively with
A pair of engaging groove 58 engages, and is arranged to the inner peripheral surface in face of guiding elements 46.
In the above method, the projection 57 and guiding elements 46 of the engagement axis 55 of the through hole 56 of admission cam shaft 31 are inserted into
Engagement groove 58 engage so that by guiding elements 46 be arranged to together with admission cam shaft 31 rotation and can into
The square upward sliding of the axes O of gas camshaft 31.Further, guiding elements 46 is arranged to revolving relative to driven member 45
Turn on direction and axis direction on relative displacement.
As shown in figures 4 and 10, governor weight 47, which is maintained at, is respectively formed at drawing in driven member 45 and guiding elements 46
Between leading groove 51 and 52, by the rotary transfer of driven member 45 to guiding elements 46.
Further, pushing member 48 by for pushed up in driven member 45 and guiding elements 46 side close to each other from
The motive force of dynamic component 45 and guiding elements 46 is applied at least one (in this implementation in driven member 45 and guiding elements 46
It is guiding elements 46 in example).In addition, circlip 49 attaches to the end of the axle portion 31A of admission cam shaft 31, to pass through packing ring
50 keep pushing member 48.
In more detail, as shown in Fig. 4,10 and 13, driven member 45 has multiple radial directed grooves 51, the radial directed
Groove 51 be formed in cam driven sprocket wheel 20 on the inner surface of guiding elements 46.Guide recess 51 act as guiding centrifugation
Counterweight 47, and side in a circumferential direction is formed in a manner of the inclined angle, θ relative to driven member 45
For uniform thickness.
As shown in Fig. 4,10 and 14, guiding elements 46 faces the surface of driven member 45 formed with multiple radial directeds at it
Groove 52.Guide recess 52 act as guiding governor weight 47 and is arranged along the radial direction of guiding elements 46.In addition, draw
Each in groove 52 is led with inclined-plane, in inclined-plane, depth of groove radially outward reduces in guiding elements 46, and tiltedly
Face is radially outward more precipitous in guiding elements 46.That is, the inclined-plane of the depth of groove of guide recess 52 is arranged to meet
Following relation：β>α, wherein α are the radially inner inclined-planes (inclination) of guiding elements 46, and β is the radial direction of guiding elements 46
Outside inclined-plane (inclination).Inclined-plane α and β is smooth in the part of a point (the point X of Figure 14 B) for the bottom of close control groove 52
Ground changes.The inclined-plane α and β of guide recess 52 allow the guide recess 51 of driven member 45 and the guide recess 52 of guiding elements 46
Bottom it is radially outward close to each other.
More specifically, in the guide recess 52 of guiding elements 46, the radially-inwardly surface of inclined-plane α passes through with regulation song
The curved surface of rate P extends to the radially outer surface of inclined-plane β.As shown in Figure 14 C, the curved surface of passing point X is to provide
Curvature p-shaped is into and the opposite side (radially inwardly and radially outwardly) of curved surface is by the surface composition of inclined-plane α and β.
Governor weight 47 shown in Fig. 4 and 10 is formed as spherical by the material with big proportion, such as iron and tungsten.In addition,
Although disc spring is used as pushing member 48 in the present embodiment, wavy leaf spring, helical spring (volute spring) etc. can be used.
Further, as shown in figures 4 and 10, circlip 49 is connected to the end of the axle portion 31A of admission cam shaft 31, to pass through packing ring 50
Pushing member 48 is supported, so as to be maintained between circlip 49 and guiding elements 46, so that the motive force of pushing member 48
It is applied to guiding elements 46.
In the phase variable mechanism 44 with said structure and construction, when centrifugal force is acted on governor weight 47,
As shown in Figure 10, governor weight 47 is in the guide recess 51 and 52 being respectively formed in driven member 45 and guiding elements 46
It is moved radially outward.Therefore, the motive force of the resistance of guiding elements 46 pushing member 48 edge on the direction away from driven member 45
The axes O movement of the admission cam shaft 31 of camshaft 17, and the inclination angle for the guide recess 51 for passing through driven member 45
(angle, θ) is relative to the relative displacement in a rotational direction of driven member 45.Therefore, the phase phase of the direction of rotation of admission cam 15
Change for bent axle 5, so as to change the valve timing of intake valve 13 by admission cam 15.
The function of the present embodiment explained below and/or operation.
As shown in Figure 15 A to 15C, when engine 10 is in low engine speed range, the centrifugal force on governor weight 47 is acted on
It is small.Therefore, the inclined-plane α for the guide recess 52 that governor weight 47 passes through guiding elements 46 and the motive force of pushing member 48 are stopped
Stay in initial position, i.e. the radially-inwardly end of guide recess 51 and 52.Therefore, the rotation of the admission cam shaft 31 of camshaft 17
The phase for turning direction becomes identical with cam driven sprocket wheel 20 (or bent axle 5), and is integrally provided at admission cam shaft
Admission cam 15 in 31 utilizes the phase driven intake valve 13 having when assembling.In this way, intake valve 13 and air bleeding valve
14 have for low and middling speed and with the valve timing of big valve overlap, and therefore, the moment of torsion increase of middling speed.
As shown in figure 16, when engine 10 reaches high engine speed range, the centrifugal force being applied on governor weight 47 increases, from
And governor weight 47 is set to be moved radially outward in the guide recess 51 of driven member 45 and the guide recess 52 of guiding elements 46.
Therefore, guiding elements 46 resists the position of the motive force inclined-plane α and β that pass through guide recess 52 of pushing member 48 to camshaft 17
(direction of arrow A) axially outward it is mobile.
At this time, in the guide recess 51 of driven member 45, relative to the inclination of the angle, θ (with reference to figure 13) of radial direction
Side in a circumferential direction is set, thus guiding elements 46 relative to driven member 45 on the incline direction of guide recess 51
Relatively steering angle θ on (direction of the arrow B in Figure 16 B and 16C).It is opposite with the direction of the arrow B of Figure 16 B and 16C
Direction be by the direction of rotation R of the rotating camshaft 17 of driving force of bent axle 5.
In the above method, the phase in the direction of rotation of the admission cam shaft 31 of camshaft 17 is by using engagement axis 55
Couple with engagement groove 58 with guiding elements 46 and change relative to bent axle 5.At this time, the phase change of admission cam shaft 31 to
Direction (spark retard side) opposite the direction of rotation R of camshaft 17.Therefore, in admission cam shaft 31 whole installation air inlet
The driving of cam 15 is in from the intake valve 13 in the phase when the phase change for being assembled to spark retard side.
Therefore, intake valve 13 and air bleeding valve 14 have for high speed and with the valve timing of small valve overlap, with increase
The output of engine 10 and improve fuel consumption, therefore reduce the discharge of harmful substance.
If the rotary speed of engine 10 reduces, the centrifugal force acted on governor weight 47 diminishes.Therefore, pushing member
48 motive force goes above the centrifugal force for making guiding elements 46 move in the direction of arrow, and therefore, guiding elements 46
Driven member side is moved to by the effect of the motive force of pushing member 48, and governor weight 47 is in guide recess 51 and 52
In move radially inwardly.Then, each in guiding elements 46 and governor weight 47 returns to the initial position shown in Figure 15.
When governor weight 47 returns to initial position, guiding elements 46 relative to driven member 45 advanced ignition side (with
The side of the arrow B of Figure 16 B and 16C are in the opposite direction) relatively turn to, and the phase of the admission cam shaft 31 of camshaft 17
Effect of the position by engaging axis 55 and engagement groove 58 changes relative to bent axle 5 arrives advanced ignition side.Therefore, intake valve 13 and row
Air valve 14, which has, is used for low and middling speed and with the valve timing of big valve overlap, therefore increases the torsion described above in middling speed
Square.
According to structure as described above and the present embodiment of construction, following beneficial effect (1) to (4) can be obtained.
(1) as shown in figures 4 and 10, in phase variable mechanism 44, due to the motive force by resisting pushing member from
The effect of mental and physical efforts causes governor weight 47 to move, and guiding elements 46 is relative to driven member 45 on direction of rotation and axis direction
Displacement, therefore relatively change relative to bent axle 5 phase on the direction of rotation of admission cam 15.Therefore, even in including dividing
In the valve mechanism 12 of the SOHC types of the liftoff camshaft 17 for being provided with admission cam shaft 31 and exhaust cam shaft 32, also can
It is enough during the rotation process of admission cam 15 and exhaust cam 16 using simple structure reliably change intake valve 13 or
The valve timing of air bleeding valve 14.Therefore, it is possible to allow the operability of the change of the valve timing relative to intake valve 13 and air bleeding valve 14
Can be stable, so as to improve the reliability and response performance of change.
(2) projection 57 is arranged on the opposite end of engagement axis 55, and projection 57 is inserted into the admission cam shaft 31 of camshaft 17
Through hole 56, and engaged with the engagement groove 58 being formed in the inner peripheral surface of guiding elements 46, and therefore, guiding elements
46 can integrally rotate with admission cam shaft 31.Therefore, linked each other by keyway with admission cam shaft 31 and guiding elements 46
The situation of link is compared, and the link between admission cam shaft 31 and guiding elements 46 can be realized by simple structure, and
Therefore, it is possible to reduce the manufacture cost of phase variable mechanism 44 (that is, valve mechanism 12).Further, since engagement axis 55 by with into
The different material of gas camshaft 31 is formed, and engagement axis 55 can be formed by the material with fabulous wearability.Therefore, it is possible to improve
The wearability and sliding of link (connection) part between the admission cam shaft 31 and guiding elements 46 of camshaft 17.
(3) as shown in Fig. 7,9 and 11, stop pin 33 is prominent on the admission cam shaft 31 in camshaft 17, and is vented
Camshaft 32 is formed with the latch recess 34 for locking the stop pin 33.Latch recess 34 is to allow 31 He of admission cam shaft
Set between exhaust cam shaft 32 along the size of direction of rotation relative displacement in the prescribed limit of angle δ.Therefore, it is possible to hold
Change places and assemble admission cam shaft 31 and exhaust cam shaft 32.In addition, even if applying excessive moment of torsion makes phase variable mechanism 44
Governor weight 47 is removed from the guide recess 51 of driven member 45 and the guide recess 52 of guiding elements 46,31 He of admission cam shaft
Rotating against between exhaust cam shaft 32 is adjusted by stop pin 33 and latch recess 34.Therefore, it is possible to pass through admission cam 15
And exhaust cam 16 prevents the big difference of the valve timing between intake valve 13 and air bleeding valve 14.
(4) as shown in figures 4 and 10, the axle portion 31A of the admission cam shaft 31 of camshaft 17 is formed with the main oil to communicate with each other
Groove 38 and secondary oily groove 39, and the outlet 40 of secondary oily groove 39 is relative to the cunning in exhaust cam shaft 32 and axle portion 31A
Annular groove 42 in dynamic surface 41 connects.Therefore, it is possible to prevent axle portion 31A and exhaust cam shaft 32 in admission cam shaft 31
Between abrasion occur and fray, therefore, it is possible to smoothly perform the opposite rotation between admission cam shaft 31 and exhaust cam shaft 32
Turn.
Further, it should be noted that although the invention has been described above with reference to the preferred embodiment of the present invention, embodiment
It is only to be rendered as an example, and the invention is not limited in this embodiment.In the purport and power without departing from the present invention
In the case of the scope that profit requires, the present invention can do various changes and modifications.
For example, in the above-described embodiments, although stop pin 33 is arranged to dash forward from the cam forming portion 31B of admission cam shaft 31
Go out, and latch recess 34 is formed on the side surface of exhaust cam 16 of exhaust cam shaft 32, and stop pin 33 can be arranged to
Protruded from the side surface of the exhaust cam 16 of exhaust cam shaft 32, and latch recess 34 can be formed in admission cam shaft 31
In cam forming portion 31B.
In addition, can be used with lower structure or construction, component 31 is formed as the row with exhaust cam whole installation
Gas camshaft, and component 32 is formed as the admission cam shaft that is integrally formed with admission cam, so that exhaust cam shaft
It is arranged to integrally rotate with guiding elements 46 by engaging axis 55, and admission cam shaft is fixed to driven member 45.Therefore,
For example, during the high speed operation of engine 10, phase variable mechanism 44 makes on the direction of rotation of exhaust cam relative to bent axle 5
Phase place change is to advanced ignition side, and the valve timing of intake valve 13 and air bleeding valve 14 is changed to for small valve overlap
Valve timing for high speed.
Claims (6)
1. a kind of valve mechanism of engine, comprising：
The intake valve and air bleeding valve of engine；
Camshaft, the camshaft are provided with admission cam and exhaust cam, and the admission cam and the exhaust cam pass through
The bent axle rotation of the engine, so as to open and close the intake valve and the air bleeding valve respectively；With
Phase variable mechanism, the phase variable mechanism make the phase of the direction of rotation of the admission cam or the exhaust cam
Position changes relative to the bent axle；
The valve mechanism of the engine is characterized in that,
The camshaft includes：Admission cam shaft, the admission cam shaft are provided with the admission cam；And exhaust cam shaft,
The exhaust cam shaft is provided with the exhaust cam, and the admission cam shaft and the exhaust cam shaft are adapted to
Enough relative displacements on the direction of rotation；And
Wherein, the phase variable mechanism includes：Driven member, the driven member are fixed on the exhaust cam shaft or institute
State on admission cam shaft and rotated by the bent axle；Guiding elements, the guiding elements are configured to and the admission cam shaft
Or the exhaust cam shaft rotates together, and can relative to the driven member on direction of rotation and axis direction it is opposite
Displacement；Governor weight, the governor weight are arranged between the driven member and the guiding elements；And pushing member, institute
State pushing member be configured to make the driven member and guiding elements side close to each other push up it is described driven
Component and the guiding elements, and
The motive force that the pushing member is resisted due to centrifugal force causes the governor weight to move, thus the guiding elements phase
Relative displacement occurs on direction of rotation and axis direction for the driven member, so that the admission cam or described
Phase changes exhaust cam relative to the bent axle in a rotational direction.
2. the valve mechanism of the as claimed in claim 1 engine, it is characterised in that wherein, the exhaust cam shaft coaxially cloth
Put in the outside of a part for the admission cam shaft.
3. the valve mechanism of engine as claimed in claim 1, it is characterised in that wherein, on the camshaft in sequence
It is provided with the admission cam, the exhaust cam and the phase variable mechanism.
4. the valve mechanism of engine as claimed in claim 2, it is characterised in that wherein, on the camshaft in sequence
It is provided with the admission cam, the exhaust cam and the phase variable mechanism.
5. the valve mechanism of the engine as described in any one of Claims 1-4, it is characterised in that wherein, the air inlet is convex
One in wheel shaft and the exhaust cam shaft is provided with stop pin, and another is formed with for locking the stop pin
Latch recess；Wherein, the latch recess is sized to allow for the admission cam shaft and the exhaust cam shaft to revolve
Turn the relative displacement in prescribed limit on direction.
6. the valve mechanism of engine as claimed in claim 2, it is characterised in that wherein, the admission cam shaft is formed with oil
Groove, and the exhaust outlet of the oily groove is arranged on the cunning with the admission cam shaft sliding contact of the exhaust cam shaft
Dynamic surface.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-189040 | 2014-09-17 | ||
| JP2014189040A JP6248876B2 (en) | 2014-09-17 | 2014-09-17 | Engine valve gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105422205A CN105422205A (en) | 2016-03-23 |
| CN105422205B true CN105422205B (en) | 2018-04-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510594564.7A Active CN105422205B (en) | 2014-09-17 | 2015-09-17 | The valve mechanism of engine |
Country Status (2)
| Country | Link |
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| JP (1) | JP6248876B2 (en) |
| CN (1) | CN105422205B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6834196B2 (en) * | 2016-07-05 | 2021-02-24 | スズキ株式会社 | Variable valve mechanism, engine and motorcycle |
| US10184360B2 (en) * | 2017-02-16 | 2019-01-22 | Borgwarner Inc. | Pressed extruded pulley |
| WO2020183486A1 (en) * | 2019-03-13 | 2020-09-17 | Tvs Motor Company Limited | An internal combustion engine |
| CN110173319B (en) * | 2019-05-21 | 2024-03-22 | 金华市隆泰动力有限公司 | Centrifugal automatic control variable exhaust valve structure |
| AT523276B1 (en) * | 2019-12-20 | 2021-07-15 | Avl List Gmbh | Camshaft adjusting device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1789674A (en) * | 2004-12-15 | 2006-06-21 | 奇瑞汽车有限公司 | Engine camshaft |
| CN202768093U (en) * | 2012-08-24 | 2013-03-06 | 重庆大学 | Air intake phase continuous adjustable mechanism of single-cylinder single overhead camshaft engine |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4331977A1 (en) * | 1993-09-21 | 1995-03-23 | Porsche Ag | Variable valve timing |
| JP2006170117A (en) * | 2004-12-17 | 2006-06-29 | Yamaha Motor Co Ltd | Valve timing control device, engine device and vehicle having this control device |
| JP2009185656A (en) * | 2008-02-05 | 2009-08-20 | Suzuki Motor Corp | Valve gear for engine |
| JP2010031855A (en) * | 2008-06-27 | 2010-02-12 | Suzuki Motor Corp | Valve gear for engine |
| JP5724669B2 (en) * | 2011-06-23 | 2015-05-27 | スズキ株式会社 | Engine valve gear |
-
2014
- 2014-09-17 JP JP2014189040A patent/JP6248876B2/en active Active
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- 2015-09-17 CN CN201510594564.7A patent/CN105422205B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1789674A (en) * | 2004-12-15 | 2006-06-21 | 奇瑞汽车有限公司 | Engine camshaft |
| CN202768093U (en) * | 2012-08-24 | 2013-03-06 | 重庆大学 | Air intake phase continuous adjustable mechanism of single-cylinder single overhead camshaft engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2016061207A (en) | 2016-04-25 |
| CN105422205A (en) | 2016-03-23 |
| JP6248876B2 (en) | 2017-12-20 |
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