CN109952416A - Camshaft for internal combustion engine - Google Patents
Camshaft for internal combustion engine Download PDFInfo
- Publication number
- CN109952416A CN109952416A CN201780062263.7A CN201780062263A CN109952416A CN 109952416 A CN109952416 A CN 109952416A CN 201780062263 A CN201780062263 A CN 201780062263A CN 109952416 A CN109952416 A CN 109952416A
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- China
- Prior art keywords
- cam
- cam contour
- camshaft
- axis
- contour element
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
- F01L13/085—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio the valve-gear having an auxiliary cam protruding from the main cam profile
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
Abstract
The present invention relates to a kind of camshaft (10), are mounted at both ends, and for the outlet valve (70) of internal combustion engine, the camshaft has cam (11) and relieving mechanism (20).The cam (11) limits cam contour (16), the outlet valve is periodically activated for the rotation by the camshaft, and including cam body (12) and cam contour element (40).Cam contour element (40) can be moved to the first cam contour position and the second cam contour position relative to cam body (12) as follows, that is: so that cam contour (16) has the first cam profile when cam contour element (40) are in the first cam contour position, and when cam contour element is in the second cam contour position with the second cam profile for being different from the first cam profile.Relieving mechanism (20) for cam contour element (40) is configured under lower first revolving speed of the camshaft cam contour element being maintained at the first cam contour position, and the cam contour element is maintained at the second cam contour position under higher second revolving speed.
Description
Technical field
One aspect of the present invention is related to a kind of camshaft of exhaust valve for internal combustion engine.According on one side, this is convex
Wheel shaft has moveable cam contour element, obtains cam contour shape relevant to revolving speed by means of the cam contour element
Shape.
Background technique
It is generated by means of camshaft with fixed stroke height and the intake and exhaust valves of stroke duration
The valve mechanism of valve stroke is normally used in internal combustion engine.However, such valve mechanism is in the different load to internal combustion engine
There are disadvantages in terms of the optimal adaptation of range.Once camshaft will activate in addition, engine is started during starting stage
Valve mechanism；However, the energy for the gas in compression and combustion room must be applied by starting engine, this may be in the phase of starting
Between cause it is unfavorable.
In order to adapt to such demand, it is allowed for the improved valve stroke curve started there are many valve mechanism.One
Kind is extremely simple but effective design is based on following camshaft, it may be assumed that in order to activate valve, which includes being arranged side by side
Several cam rails, and the camshaft can carry out transverse shift by means of adjustment unit.Then, suitable for the convex of corresponding demand
Wheel track can be selected by the transverse shift of camshaft.In the case where the camshaft for exhaust valve, for example, can be by
If under type setting is for a cam of starting stage and for the additional cams of normal operating, it may be assumed that wherein, for starting rank
The cam of section provides additional valve opening, to reduce the gas pressure in combustion chamber.
However, such adjustment unit increases space and the weight demands of valve mechanism, and need to adjustment unit
Carry out complicated control.Furthermore, it is also possible to damage the stability and intensity of camshaft.
JP 2008-82188 describes a kind of camshaft, has the function of decompression and for phase shift, the decompression function
It can depend on the revolving speed of camshaft.Wherein, control shaft 57 is rotated by means of centrifugal mechanism 50 relative to cam 36, to be promoted
65a and 65b(is sold referring to Fig. 6, Fig. 7 of JP 2008-82188).The mechanism need together with kinematic link 59 be attached to this from
The tension spring 53 of concentric mechanism, and therefore, there is bigger space requirement.
Further, since control shaft 53 is arranged on rotation axis, at least one shaft end of camshaft must be it is come-at-able,
This leads to the limitation of installation and placement to camshaft.
Summary of the invention
The present invention have a kind of target of camshaft is provided, the camshaft on the one hand be it is adjustable, but then, subtract
At least some of few disadvantages mentioned above.
According to an aspect of the present invention, camshaft is especially provided the exhaust valve for internal combustion engine.The camshaft packet
Include cam and the trigger mechanism for its cam contour element.The cam limits cam contour, for by rotating the camshaft
Periodically to activate exhaust valve.The cam includes cam body and the cam contour element.The cam contour element can
It is moved to the first cam contour position and the second cam contour position relative to cam body, so that if at cam contour element
In the first cam contour position, then the cam contour has the first cam profile, and if at cam contour element
In the second cam contour position, then the cam contour has the second cam contour shape different from the first cam profile
Shape.The trigger mechanism is configured under lower first camshaft speed (in particular, under first range of speeds) for institute
It states cam contour element and is maintained at the first cam contour position, and (in particular, under higher second camshaft speed
Under two ranges of speeds, it is higher than the first revolving speed or velocity interval) the cam contour element is maintained at the second cam contour position
It sets.
The camshaft has bearing on two sides, that is, it has first bearing and second bearing, for around the cam
The camshaft axis of axis is pivotably supported the camshaft, wherein the cam is axially arranged between these bearings.Root
According to the present invention, the trigger mechanism is also disposed between these bearings.
Preferably, the cam contour element is prominent in the first cam contour position, for activate (opening) exhaust valve (with
Surrounding cam contour is opposite), and in the second cam contour position, it is not prominent or protrusion is less, so that exhaust valve is not subjected to
Any, i.e. any substantive additional actuating (opening)；It therefore, will not be than the cam contour by means of cam contour component ambient
Further open.
Second range of speeds is substantially close to first range of speeds, wherein first range of speeds and second range of speeds
Between conversion can be with threshold value or with specific transitions (transition range) Lai Dingyi.Therefore, the trigger mechanism is configured to
Cam contour element is maintained at the first cam contour position lower than in the case where predetermined threshold or transition range by revolving speed, and
Revolving speed is more than that cam contour element is maintained at the second cam contour position in the case where predetermined threshold or transition range.According to one
A aspect, the trigger mechanism be configured to from the first revolving speed to the second revolving speed (or from first range of speeds to the second revolving speed
Range) transition period take cam contour element to second cam contour position from the first cam contour position.
For example, the first revolving speed can be located in the typical range of speeds for starting.According on one side, also depend on
First revolving speed of engine type is between 0rpm and 1,000rpm, and preferably between 0rpm and 500rpm.Second turn
Speed can be located in the normal operation range of engine, in each case relative to the revolving speed of camshaft, higher than about
500rpm, and preferably higher than 700rpm or 1,000rpm.Therefore, the threshold value can be located at for example between 500rpm and 1,
In the range of speeds between 000rpm.
Therefore, camshaft according to the present invention allows cam profile relevant to revolving speed, and therefore, allows to be vented
The valve stroke curve relevant to revolving speed of door.According to a particular aspects, under the slow-speed of revolution typical for starting stage,
Cam contour element is prominent (in the first cam contour position), so that realizing additional valve opening (with higher revolving speed or the
Compare two cam contour positions) so that needing the pressure starter motor in combustion chamber using less effort.
According to an aspect of the present invention, can realize in the case where the transverse shift of not cam should be related to revolving speed
Cam profile.Particularly, this enables camshaft to install on two sides.Installation on two sides makes it possible to especially
Power is transmitted advantageously between cam and valve, this is because avoiding the undesirable bending vibration of camshaft, and energy
It is enough neatly to control valve mechanism.
First cam profile can be different from the second cam profile, particular in that the first cam profile
With protruding portion, to open exhaust valve (70) during the compression travel of internal combustion engine.The protruding portion preferably takes up described convex
The rotation angle range between 1 ° and 30 ° of wheel shaft.The protruding portion is preferably centered on phase on the direction of rotation of cam
Maximum eccentricity or angle (protruding portion of cam body) for cam contour bias the angle between 90 ° and 270 °,
Particularly preferably bias the angle between 90 ° and 180 °.
The cam contour element preferably (in axial direction) is mounted in cam in center.
Herein, "one" always refers to "at least one"；For example, " cam "=" at least one cam " etc..The
One range of speeds may include static (revolving speed 0).
In dependent claims and to showing other expedients in being described below of attached drawing.There, embodiment
Various aspects and the appended drawing reference of details attached drawing indicate；However, these appended drawing references are only shown and are for the purpose of illustration.
Unrelated with the embodiment presented, aspect can also be combined with other aspects.
Detailed description of the invention
It is as follows shown in attached drawing:
Fig. 1 shows the perspective view of the valve mechanism according to an embodiment of the invention for exhaust valve；
Fig. 2 shows the front views according to the valve mechanism of Fig. 1；
Fig. 3 a-c shows the side view of the valve mechanism according to Fig. 1 and Fig. 2, and wherein cam contour element is in the first cam wheel
Wide position；
Fig. 4 a-c shows the side view of the valve mechanism according to Fig. 1 and Fig. 2, and wherein cam contour element is in the second cam wheel
Wide position；
Fig. 5 shows another side sectional view of the cam of Fig. 4 b；And
Fig. 6 shows the valve stroke figure of valve mechanism according to the present invention.
Specific embodiment
Figures 1 and 2 show that the exhaust for internal combustion engine with camshaft 10 according to an embodiment of the invention
The valve mechanism of door 70.Camshaft 10 includes cam 11, is arranged to actuating exhaust valve 70.Camshaft 10 can be revolved around its axis
Turn.For this purpose, camshaft 10 is supported in cylinder head by bearing 8a, 8b, therefore propped up on two sides by bearing 8a, 8b
Support.Therefore, it is overhead camshaft.Camshaft 10 further includes centrifugal elements 21, is come below in relation to Fig. 3 and Fig. 4 more detailed
Ground description.
Installation part 8a, 8b on two sides allow the advantageous power between cam and valve to transmit, this is because keeping away
The undesirable bending vibration of camshaft is exempted from.Installation part on two sides also allows for neatly controlling valve mechanism；
According to a preferred aspect, the transmission gear or chain conveyer sprocket wheel that are connected to the crankshaft of internal combustion engine are located at the side 7a of camshaft
On, and the output gear for being connected to inlet valve drive shaft is located on the other side 7b of camshaft 10.This allows the cam
Axis is in valve mechanism described in such as DE 102005057127.
The valve mechanism further includes the mechanism for activating exhaust valve 70 by cam 11.Shown in fig. 1 and 2
Embodiment in, the mechanism include be arranged in cam 11 and export valve 70 between rocker arm 60 and gasket 72 so that the outlet
Valve is activated via rocker arm 60 and tappet 72 by cam 11.Fig. 2 also shows valve spring 74, makes valve 70 against convex
11 biasing (at least by stages, for example, in the case where valve is activated) of wheel, and therefore, valve 70 and cam 11 it
Between generate force closure.In the stage that valve is not activated, valve is pressed into valve seating by valve spring, which applies
Corresponding reaction force.
As can be seen in Figure 2, cam 11 includes cam body 12 and cam contour element 40(referring to Fig. 3 b, figure
4b；In Fig. 2, it is only capable of seeing one end of the cam contour element as relief surface 44), the cam body 12 and cam contour
Element 40 limits the cam contour 16 of cam 11 together.More precisely, decompression of the cam contour 16 by cam contour element 40
Surface 44(is also appointed as the cam contour surface of cam contour element) and cam body 12 remaining cam contour surface 14
It is formed.Cam contour 16 is the section profile of cam 11, which activates exhaust valve in the case where camshaft 10 rotates
70, and therefore, the valve stroke curve of exhaust valve 70 is had decisive impact.
Cam contour element 40 is designed to pin, is retractable into cam body 12 and stretches out from cam body 12
(referring also to Fig. 3 b, Fig. 4 b).
In extended position (the first cam contour position shown in Fig. 3 b), the cam contour surface of cam contour element 40
44 is prominent relative to remaining cam contour surface 14.As a result, pass through the cam contour surface 44 of cam contour element 40, outlet
Valve 70 is subjected to additional actuating (opening).In retracted position (the second cam contour position shown in Fig. 4 b), cam contour
Surface 44, which is arranged to, to be flushed with remaining cam contour surface 14 and (does not protrude substantially) so that outlet valve be not subjected to it is any
Additional actuating (opening), it means that do not have tangible actuating (opening).Therefore, cam contour 16 has variable cam wheel
Profile shape, depending on cam contour element 40 is in the first cam contour position or the second cam contour position.
As a result, the cam contour surface 44 of cam contour element 40 be disposed in cam contour 16 as in lower section, it may be assumed that
In the section, at least in the second cam contour position or in remaining cam of the section around cam contour element 40
On contour surface 14, outlet valve 70 is closed.
Therefore, the cam contour surface 44 of cam contour element 40 is used as relief surface 44；In typical starting stage
Under the slow-speed of revolution, additional valve opening (in the first cam contour position) allows the pressure in combustion chamber to be released, so as to combustion
The pressure starter motor in room is burnt to need using less effort.Under higher rotation speed typical for normal operating, it is therefore prevented that
Additional valve opening, so that the loss of engine efficiency need not be received.
As shown in Figure 2, axial direction of the cam contour element 40(relative to camshaft) in center it is mounted on cam 11
In.This center installation, especially combines with the valve mechanism with rocker arm 60, it is ensured that power is from cam 11 to valve 70
Uniform and low-loss transmitting.According to general aspect, the center of cam contour element 40 is to be less than the 20% of cam width from convex
The center deviation of wheel (relative to axial direction).
Fig. 3 and Fig. 4 illustrates in greater detail the trigger mechanism 20 of valve mechanism as shown in Figures 1 and 2, by means of this
Trigger mechanism 20, cam contour element 40 move according to revolving speed and (retract and stretch out).Therefore, trigger mechanism 20 ensures cam wheel
Wide element 40 or its cam contour surface 44 are stretched out at the low rotational speed (the first cam contour position) and (the under higher rotation speeds
Two cam contour positions) it retracts.
Fig. 3 a, Fig. 4 a are the side views from the right side in Fig. 2 as a result,；Fig. 3 b, Fig. 4 b are the plane A-A along Fig. 2
Side sectional view；And Fig. 3 c, Fig. 4 c are the side sectional views of the plane B-B along Fig. 2.Fig. 3 a-c is shown in the first cam
The cam contour element of outline position, and Fig. 4 a-c shows the cam contour element in the second cam contour position.
Fig. 3 a, the side view of Fig. 3 c or section view show the centrifugal elements 21 of trigger mechanism 20.Centrifugal elements 21 are set
It is calculated as lever, there is the first lever arm 27 and the second lever arm 28 on two sides, and centrifugal elements 21 can be revolved around axis 22
It is mounted on camshaft 10 with turning and (that is, being mounted on the suspension rotated together with camshaft 10, here, is mounted on cam body
On 12, which is rigidly connected to camshaft 10).Fig. 3 a, Fig. 3 c show the centrifugation in the first eccentric position
Element 21；In Fig. 4 a, Fig. 4 c, it is shown at the second eccentric position, in second eccentric position, 21 phase of centrifugal elements
First eccentric position is rotated clockwise around axis 22.
Biasing element 30 shown in Fig. 3 c, Fig. 4 c makes centrifugal elements 21 towards the first eccentric position (in Fig. 3 a, Fig. 4 a
In view, counterclockwise) biasing.Biasing element 30 is disposed in the opening for passing through camshaft and being laterally extended of camshaft 10
In, so that the rotation axis that the longitudinal axis of biasing element 30 passes through camshaft extends at right angle.The biasing can be by multiple
Position spring realizes that the reset spring is approximate with the longitudinal axis of biasing element 30 in camshaft 10 to be disposed concentrically upon, and is made
Biasing element 30 presss from both sides (pressure) and leans on centrifugal elements 21.The reset spring can be the opening (in retainer) for being clipped in camshaft and partially
Set the retainer on element 30() between compressed spring.
In one aspect, the slave camshaft 10 of biasing element 30 is convex towards being shorter in length than for the section outstanding of centrifugal elements 21
The camshaft radius of wheel shaft 10 at this location.This is suitable for the first eccentric position and/or the second eccentric position.This allows to bias
The particularly compact arrangement of element 30.
In the first eccentric position, centrifugal elements 21 press from both sides (pressure) by biasing element 30 and lean on the first retainer.Here, first stops
Moving part is for example formed by the middleware 26 of the first lever arm and camshaft 10 at the first lever arm.First retainer is disposed in
On the lever sides different from biasing element 30 of centrifugal elements 21.First retainer limitation centrifugal elements 21 make in biasing element 30
The pivot on direction that centrifugal elements 21 bias.The pivot of centrifugal elements 21 in the opposite direction is biased the reset bullet of element 30
The maximum compression of spring limits, or is limited by the additional retainer between the second lever arm 28 and camshaft 10.
In one aspect, biasing element 30 is connected to centrifugal elements 21 in a manner of force-fitting；Particularly, it is pressed against centrifugation
Element 21.
Centrifugal elements 21 are made to be located at resting position, Huo Zhe towards the biasing that the first eccentric position applies by biasing element 30
Under the slow-speed of revolution (the first revolving speed) of camshaft, it is located at the first eccentric position, as shown in fig. 3a.
In the shown embodiment, centrifugal elements are designed to lever.Lever 21, and especially its lever arm 27,28, ruler
It is very little to be set such that the centrifugal force acted on as the cam shaft rotates acts on the first lever arm 27 than on the second lever arm 28
It is stronger, and therefore, apply the torque towards the second eccentric position in centrifugal elements 21 as a whole (that is, in Fig. 3 a, figure
It is oriented clockwise in the view of 4a).If revolving speed is more than specific threshold (for example, being in higher second revolving speed), the torque
More than the biasing of biasing element 30, and as a result, centrifugal elements 21 are subsequently positioned at the second eccentric position, such as institute in Fig. 4 a
Show.
According on one side, the lever extends along the partial sector around camshaft 10.According to one aspect, the first thick stick
The center of gravity of lever arm 27 is more than 90 °, preferably more than 120 ° relative to the centre offset of the second lever arm 28, or is even more than
135°.According on one side, the center of gravity and/or lever end of the first lever arm 27 are relative to pivot axis 22(relative to cam
The rotation axis of axis 10 and on the spatially extended direction of centrifugal elements 21) biasing more than 90 °, preferably more than 120 °,
Or even more than 135 °.According on one side, the center of gravity and/or lever end of the second lever arm 28 are relative to pivot axis 22
Biasing is less than 90 °, and preferably less than 45 °, or even less than 30 °.According on one side, the center of gravity of the first lever arm 27 and/
Or lever end biases twice of the angle of the center of gravity or lever end more than the second lever arm 28, three relative to pivot axis 22
Times or even four times.Herein, angle always surrounds the rotation axis of camshaft 10 and prolongs in the space of centrifugal elements 21
It is limited on the direction stretched.These aspects allow lever to have sufficiently large lever arm, and at the same time having in radial directions low
Space requirement, so that compact design is possible.
According on one side, centrifugal elements (lever) 21 can be pivoted around the lever axis for being parallel to camshaft axis.According to
On one side, it arranges to the lever axis opposing cam axis eccentric axis；Preferably, its protrusion in cam body 12
Direction on radially remote from camshaft axis.The protrusion is the radial angular range since camshaft axis,
There is the angular deviation less than 30 ° on the direction of the protrusion (maximum eccentricity) of cam body 12.
According to additional aspect, centrifugal elements 21 are arranged to and 12 direct neighbor of cam, that is, therebetween without another function
Energy part, such as the bearing for cam etc..Axial distance (side according to one aspect, between centrifugal elements 21 and cam 12
Face to side) it is less than 0.5cm.According to one aspect, between the central plane of centrifugal elements 21 and the central plane of cam 12
Axial distance is less than twice of the axial width of cam or less than 1.5 times, or the axial width of even less than cam.According to one
A aspect, camshaft are supported on two sides, and centrifugal elements 21 are disposed between two bearings 8a, 8b.This makes
It can be realized compact design in axial direction.
Fig. 3 b, Fig. 4 b show cam contour element 40 and coupled connection mechanism, which is couple to centrifugal elements 21
Cam contour element 40.
This coupling is implemented so that if centrifugal elements (21) take the first eccentric position (as shown in figure 3b),
Cam contour element (40) is maintained at the first cam contour position, and if centrifugal elements (21) take the second eccentric position
(as shown in fig 4b), then cam contour element (40) is maintained at the second cam contour position.
Cam contour element 40 is designed to pin, and the blind hole of cam body 12 is at least partially disposed at along pin axis
In, and can be withdrawn into the blind hole.The surface that the slave blind hole of cam contour element 40 faces out forms cam contour surface
44.In the first cam contour position (Fig. 3 b), the pin is at least partly stretched out from blind hole, and in the second cam contour position
(Fig. 4 b), the pin are substantially retracted into blind hole, so that cam contour surface 44 is flushed with circumferential surface.
Coupled connection mechanism between centrifugal elements 21 and cam contour element 40 realized by moveable stop-motion body 24,
The stop-motion body 24 is in first or second stop position, this depends on the eccentric position of centrifugal elements 21.The stop-motion body is designed
For pin, which is rigidly connected to centrifugal elements 21 and can rotate around the axis for being parallel to camshaft axis.
According on one side, stop-motion body 24 is connected in a manner of just sealed (positive-locking), particularly rigidity
To centrifugal elements 21.According on one side, connection opposing cam axis eccentric axis between centrifugal elements 21 and stop-motion body 24
Arrangement, it is preferable that radial partially with the protruding portion or protrusion (+/- 30 ° of angular range around prominent) of cam body 12
It sets.
According on one side, by moving centrifugal elements 21 between the first and second eccentric positions, which can
To be rotated around the stop body axis for being parallel to camshaft axis.According on one side, stop-motion body 24 or stop body axis are relatively convex
Axle axis is prejudicially arranged, is preferably arranged in the protrusion of cam body 12.According to one aspect, stop body axis
It is equivalent to the lever axis of centrifugal elements (lever) 21, and stop-motion body 24 can rotate together with centrifugal elements 21.
Cam contour element 40 is biased against stop-motion body 24.The biasing is not shown, and can for example pass through reset spring
It realizes, the axis of the reset spring and cam contour element 40 is disposed concentrically upon, and cam contour element 40 is made to press from both sides (pressure)
By stop-motion body 24.The reset spring can be the retainer being clipped in the blind hole or cam body 12() and cam contour element
Retainer on 40() between compressed spring.According on one side, cam contour element 40 is connected in a manner of force-fitting
Stop-motion body 24(is pressed against it).According on one side, the contact portion between stop-motion body 24 and cam contour element 40 is disposed in
In cam body 12, it is preferably arranged in the protrusion of cam body 12.
According on one side, stop-motion body 24 is non-circular in the part that the folder of cam contour element 40 leans on stop-motion body 24.
If centrifugal elements 21 are in the first eccentric position, stop-motion body 24 is in the first stop position and is cam wheel
Wide element 40 provides the first retainer, which limits the first cam contour position for being used for cam contour element 40.
If centrifugal elements 21 are in the second eccentric position, stop-motion body 24 is in the second stop position and is cam contour element 40
The second retainer is provided, which limits the second cam contour position for being used for cam contour element 40.According to one
Aspect, the first retainer and the second retainer are different.Preferably, the second retainer is recessed relative to the first retainer.
Fig. 3 b, Fig. 4 b embodiment in, which is realized by axis 24, the axis 24 around axis 22(Fig. 3 c, figure
It 4c) rotates and is rigidly connected to centrifugal elements 21.Therefore, according to the eccentric position of centrifugal elements 21, axis 24 is rotated to
First stop position (Fig. 3 b) or the second stop position (Fig. 4 b).
Cam contour element 40 is pin, is mounted in cam 11, can be shifted along cam contour element axis, and against
The biasing of axis (stop-motion body) 24 (that is, along second cam contour location bias of direction or direction of cam body 12).
Based on this biasing, therefore cam contour element 40 takes retainer using position specified by axis 24.In axis 24
The first stop position (Fig. 3 b), retainer generated by the section relatively more outstanding of axis 24.This prevents cam contour element
40 are moved in cam body 12 (towards the second cam contour position), so that cam contour element 40 is in the first cam contour
Position, that is, its cam contour surface 44 is prominent relative to remaining cam contour surface 14.
In the second stop position (Fig. 4 b), the section that retainer passes through the relatively fewer protrusion of axis 24 or flattens is generated.This
Release cam contoured component 40 is moved in cam body 12 (towards the second cam contour position), and due to the biasing,
Therefore cam contour element 40 is in the second cam contour position, that is, it will not be prominent with its cam contour surface 44.
In this way, it realizes under the slow-speed of revolution (the first revolving speed), cam contour surface 44 is prominent, and therefore, draws
The additional actuating for playing exhaust valve 70, as shown in Fig. 3 a-3c, and under higher rotation speed (the second revolving speed), cam contour surface
44 flush with remaining cam contour surface 14, and it is therefore prevented that exhaust valve 70 additional actuating.
Referring to Fig. 5, the position of cam contour element 40 will more accurately be described.As already mentioned, cam contour element
40 cam contour surface, more precisely, the center 44' on the cam contour surface, is preferably arranged in cam contour 16
At lower section, it may be assumed that at the section, at least in the second cam contour position or in remaining cam contour table of the section
In face, outlet valve is closed.
The cam contour surface of cam contour element 40 is preferably arranged in the pressure for distributing to internal combustion engine of cam contour 16
In the section of indention journey.
Angle [alpha] between the maximum eccentricity 16a of cam contour 16 and the center 44' on cam contour surface is preferably less than
180 ° (measured along direction of rotation as shown in Figure 5, wherein the direction of rotation be it is clockwise, as based in Fig. 3 b and Fig. 4 b
Shown in rocker arm 60 it can be seen that).For example, angle [alpha] can between 90 ° and 180 °, preferably between 105 ° and 180 °,
Or even between 125 ° and 180 °.Which ensure that cam contour surface is effective as relief surface, and during starting
It can be released stress from combustion chamber.
The maximum eccentricity 16a of cam contour 16 is usually unrelated with cam contour position, and is defined as avoiding opposite
Ambiguity in the second cam contour position.
Cam contour element 40 is pin, is installed in cam 11 and can shift along cam contour element axis.It should
The axis of pin 40 is with the angle less than 45 °, preferably less than 30 ° from the camshaft of the center 44' by cam contour surface
Radial direction deviates.
The entire cam contour surface of cam contour element 40 only occupies the limited angular range of cam contour 16, preferably
Less than 45 °, particularly preferably less than 30 °, and Most particularly preferably less than 15 °.Preferably, the cam of cam contour element 40
Contour surface occupies at least 2 ° of angular range.
Referring to Fig. 6, which depict use valve mechanism according to the present invention come the valve row of the four-stroke engine operated
Cheng Tu.The valve stroke is schematically shown according to the phase angle α of cycle of engine through valve machine according to the present invention
Structure driving inlet valve (for dotted line and be labeled as I curve) and exhaust valve (for solid line and labeled as E and E' curve)
Valve opening V, phase angle α are about the half of crankshaft angles.BDC indicates bottom dead centre (in phase angle α=0 ° and α=180 °
Place), and TDC indicates the top dead-centre of crankshaft (at phase angle α=90 ° and α=270 °).The figure shows four rows in the order
The following circulation of journey engine, it may be assumed that ejection；Air inlet；Compression；Work.
The common valve stroke curve of curve E and I expression four-stroke engine.Curve E' indicates to be in the first cam wheel
The additional actuating of the cam contour element 40 of wide position.In the second cam contour position, there is no the additional actuatings, that is, curve
E' is replaced by flat curve (no valve stroke).Occur in the compression travel added before being actuated at top dead-centre.As
Description, which allows gas to escape from combustion chamber and therefore reduces pressure so as to by starter motor to pressure
The work of execution is reduced.
Fig. 6 also illustrates some general aspects of the cam contour element 40 relative to the arrangement of motor phase, this is below
It describes and is optionally suitable for any embodiment.Motor phase angle α is limited as follows as a result, it may be assumed that it is in the motor cycles phase
Between by the interval from 0 ° to 360 °.According on one side, engine is four-stroke engine, and engine phase angle α is gas
The half of door crankangle.
According on one side, the cam contour surface of cam contour element 40 is arranged for the compression travel of internal combustion engine
The valve actuation of period.According to additional aspect, the cam contour surface of cam contour element 40 is arranged in such a way, it may be assumed that
So that the phase angle α of the maximum valve stroke on the cam contour surfacePIt is located at before top dead-centre UDC at the end of compression travel big
Phase difference about in the range of 70 ° to 30 °, preferably in the range of 65 ° to 45 °.According to additional aspect, by cam wheel
Following phase intervals (the α of the covering cycle of engine of valve opening caused by the cam contour surface of wide element 40O - αC), it may be assumed that
Greater than 2 ° or be greater than 3 °, or even greater than 5 °, and/or less than 20 °, less than 15 ° or even less than 10 °, for example, 3 ° and 15 ° it
Between, and preferably between 5 ° and 10 °.α as a result,OBeing defined as valve opening is more than αPThe 10% of the maximum valve opening at place
Phase, and αCIt is defined as phase of the valve opening again below the value.In other words, phase intervals (αO - αC) it is gas
Door aperture is greater than αP10% range of the maximum valve opening at place.
According to additional aspect, cam contour element is disposed in the non-actuating portions of cam, so that in cam contour
The actuating of valve does not occur in the part of component ambient.According to additional aspect, by cam contour element (in the first cam wheel
Wide position) (maximum) valve stroke be less than through cam as a whole (that is, passing through the point 16a of cam contour；Referring to Fig. 5)
(maximum) valve stroke 30%, less than 20%, or even less than 10%.
Therefore, can have the operation of the internal combustion engine of valve mechanism as described herein, especially progress of starting sequence described below,
Wherein, appended drawing reference is referring to all attached drawings:
Initially, for example, the beginning started, camshaft 10 are rotated with low (first) speed, and it is all by means of cam 11 as a result,
Activate to phase property exhaust valve 70.Due to low (first) speed, cam contour element 40 is located at the first cam contour position, at this
Its cam contour surface 44 is prominent at first cam contour position, so that during the compression travel of internal combustion engine, 70 quilt of exhaust valve
Cam contour surface 44 activates.As described above, the first cam contour position is convex by the way that cam contour element 40 is maintained at first
The trigger mechanism 20 of outline position is taken turns to realize, as shown in Fig. 3 a-3c and described in these attached drawings.By means of prominent
Cam contour 44 out, valve is opened, and allows to reduce the gas pressure in combustion chamber.
During further, the rotation of camshaft is accelerated to higher second speed.By means of the higher speed
Degree, cam contour element 40 are moved to the second cam contour position (Fig. 4 a-4c), the cam wheel at the second cam contour position
Wide surface 44 is not prominent or protrusion is less.As described above, the movement of the second cam contour position of direction passes through cam contour member
Part 40 is maintained at the trigger mechanism 20 of the second cam contour position to realize, as shown in figures 4 a to 4 c and about these attached drawings
It is described.As a result, outlet valve 70 is no longer activated by the cam contour surface 44 of cam contour element 40, that is, without significant
Additional valve opening.This allows the normal operating of internal combustion engine, and the air-fuel mixture especially in combustion chamber is just
Normal pressure contracting.
Although being described above and depicting each embodiment in the accompanying drawings, protection scope is only wanted from right
It asks.In addition, the details of above-described embodiment is only illustrated for the illustrative purpose about the embodiment, but it is intended that them not
It should be associated with the embodiment discussed；On the contrary, they can also be used in association with and combine with any more generally aspect.
Claims (10)
1. the camshaft (10) of the exhaust valve (70) for internal combustion engine, wherein the camshaft includes:
For being pivotably supported the first bearing of the camshaft (10) around the camshaft axis of the camshaft (10)
(8a) and second bearing (8b)；
Cam (11), wherein the cam (11) limits cam contour (16), for by rotating the camshaft come the period
The exhaust valve being activated to property, and wherein, the cam (11) includes cam body (12) and cam contour element (40),
Wherein, the cam contour element (40) can be moved to relative to the cam body (12) the first cam contour position and
Second cam contour position, so that if the cam contour element (40) is in first cam contour position, it is described
Cam contour (16) has the first cam profile, and if the cam contour element is in second cam contour
Position, then the cam contour (16) has second cam profile different from first cam profile；And
It is used for the trigger mechanism (20) of the cam contour element (40), wherein the trigger mechanism (20) is configured in institute
It states and the cam contour element is maintained at first cam contour position under lower first revolving speed of camshaft, and
The cam contour element is maintained at second cam contour position under higher second revolving speed of the camshaft,
Wherein, the cam (11) and the trigger mechanism (20) are disposed axially in the first bearing (8a) and second axis
It holds between (8b).
2. camshaft according to any one of the preceding claims, which is characterized in that
If the cam contour element (40) is in first cam contour position, for activating the exhaust valve (70)
The cam contour element (40) it is prominent, and if the cam contour element is in second cam contour position,
Then the cam contour element (40) is not prominent or protrusion is less.
3. camshaft according to any one of the preceding claims, which is characterized in that the trigger mechanism (20) include from
Heart element (21) and coupled connection mechanism (24), wherein
The centrifugal elements (21) are mounted to take the first eccentric position under lower first revolving speed of the camshaft,
And the second eccentric position, and its are taken by the effect of centrifugal force under higher second revolving speed of the camshaft
In,
The centrifugal elements (21) are couple to the cam contour element (40) by the coupled connection mechanism (24), so as to it is described from
Heart element (21) takes in the case where first eccentric position that the cam contour element (40) is maintained at described first is convex
Outline position is taken turns, and in the case where the centrifugal elements (21) take second eccentric position by the cam contour member
Part (40) is maintained at second cam contour position.
At least one of 4. camshaft according to claim 3, which is characterized in that in following (a) to (c):
(a): the centrifugal elements (21) are levers, and the lever is mounted on as follows on the camshaft (10), even if
The centrifugal force acted on during the rotation of the camshaft is obtained to apply on the lever (21) towards second eccentric position
Torque, and the trigger mechanism (20) has biasing element (30), and the biasing element (30) is by the lever (21) court
It is biased to first eccentric position, wherein the biasing element (30) is connected to the centrifugal elements in a manner of force-fitting
(21), the centrifugal elements (21) especially are pressed against by means of compressed spring；
(b): the centrifugal elements (21) be can around the lever axis pivotable lever for being parallel to the camshaft axis and extending,
In, the preferably relatively described camshaft axis of the lever axis is prejudicially arranged, wherein the lever axis is particularly preferably
It is separated on the direction of the protrusion of the cam body (12) with the camshaft axis；
(c): the centrifugal elements (21) are arranged to and the cam (12) direct neighbor.
5. the camshaft according to any one of claim 3 and 4, which is characterized in that preferably, below in (d) and (e)
At least one of:
(d): the coupled connection mechanism (24) is connected to the centrifugal elements (21), for being in described in the centrifugal elements (21)
Prevent the cam contour element (40) mobile towards second cam contour position in the case where first eccentric position, and
For discharging cam contour element (40) court in the case where the centrifugal elements (21) are in second eccentric position
It is mobile to second cam contour position, wherein
The cam contour element (40) is towards the second cam contour location bias；
(e): the coupled connection mechanism includes stop-motion body (24), and the cam contour element (40) is inclined against the stop-motion body (24)
Set, and the stop-motion body (24) is connected to the centrifugal elements (21) in just sealed, particularly rigid mode, so as to institute
It states centrifugal elements (21) and correspondingly takes first eccentric position or second eccentric position together, so as to for example can be with
The centrifugal elements (21) together around described in (b) lever axis rotation, wherein the stop-motion body (24) described first from
Heart position is the cam contour element (40) the first retainer of offer, and is the cam wheel in second eccentric position
Wide element (40) provides second retainer different from first retainer, wherein the stop-motion body (24) is preferably opposite
The camshaft axis is prejudicially arranged.
6. camshaft according to any one of the preceding claims, which is characterized in that the cam contour element (40) is
Pin, the pin is displaceably mounted in the cam (11) along cam contour element axis, and towards second cam
Outline position biasing.
7. being used for the valve mechanism of internal combustion engine, there is camshaft according to any one of the preceding claims, wherein described
Camshaft (10) is connected to transmission gear in the axially outer of first bearing (8a), drives for the crankshaft by the internal combustion engine
It is dynamic, and it is connected to output gear in the axially outer of second bearing (8b), for driving inlet valve actuating unit.
8. internal combustion engine, with valve mechanism according to claim 7, wherein transmission gear is connected to crankshaft, and its
In, output gear is connected to inlet valve actuating unit.
9. the method for the exhaust valve (70) for activating internal combustion engine, wherein the internal combustion engine has camshaft (10), the cam
Axis (10) has cam (11), wherein the cam (11) has cam body (12) and can be relative to the cam body
(12) mobile cam contour element (40),
Wherein, the camshaft (10) is by means of first bearing (8a) and second bearing (8b) around the cam of the camshaft (10)
Axis axis is rotatably mounted so that the cam (11) and trigger mechanism (20) be disposed axially in the first bearing (8a) and
Between the second bearing (8b),
Wherein, which comprises
Rotate the camshaft (10) with First Speed, for periodically activating the row by the cam (11)
Valve, wherein the cam contour element (40) is in the first cam contour position, at first cam contour position,
The cam contour surface (44) of the cam contour element (40) is prominent, so that during the compression travel of the internal combustion engine, institute
Exhaust valve (70) is stated to be activated by the cam contour surface (44)；
By the second speed of the camshaft spun up higher than the First Speed,
The cam contour element (40) is moved to the second cam contour position by means of the trigger mechanism (20), in institute
It states at the second cam contour position, the cam contour surface (44) is not prominent or protrusion is less, so that the exhaust valve (70)
No longer activated by the cam contour surface (44) of the cam contour element (40).
10. the use of camshaft according to any one of claim 1 to 7 or valve mechanism according to claim 8
In in particular according to method as claimed in claim 9 come activate internal combustion engine exhaust valve purposes.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016119105.1 | 2016-10-07 | ||
| DE102016119105.1A DE102016119105A1 (en) | 2016-10-07 | 2016-10-07 | Camshaft for internal combustion engine |
| PCT/EP2017/075544 WO2018065602A1 (en) | 2016-10-07 | 2017-10-06 | Camshaft for combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109952416A true CN109952416A (en) | 2019-06-28 |
| CN109952416B CN109952416B (en) | 2021-11-16 |
Family
ID=60022120
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780062263.7A Active CN109952416B (en) | 2016-10-07 | 2017-10-06 | Camshaft for internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3523513B1 (en) |
| CN (1) | CN109952416B (en) |
| BR (1) | BR112019006860A2 (en) |
| DE (1) | DE102016119105A1 (en) |
| WO (1) | WO2018065602A1 (en) |
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|---|---|---|---|---|
| US3381676A (en) * | 1967-04-12 | 1968-05-07 | Tecumseh Products Co | Compression relief mechanism |
| US5682847A (en) * | 1995-10-12 | 1997-11-04 | Unisia Jecs Corporation | Valve actuating device for engine |
| EP1247950A2 (en) * | 2001-03-30 | 2002-10-09 | Tecumseh Products Company | Mechanical compression and vacuum release |
| EP1892388A1 (en) * | 2006-08-08 | 2008-02-27 | HONDA MOTOR CO., Ltd. | Engine with decompression device |
| JP2008082188A (en) * | 2006-09-26 | 2008-04-10 | Honda Motor Co Ltd | Valve gear of internal combustion engine |
| US20090301419A1 (en) * | 2008-06-10 | 2009-12-10 | Kawasaki Jukogyo Kabushiki Kaisha | Decompression Mechanism |
| CN202117726U (en) * | 2011-08-29 | 2012-01-18 | 重庆银钢汽车配件制造有限责任公司 | Camshaft structure |
| CN102486101A (en) * | 2010-12-06 | 2012-06-06 | 现代自动车株式会社 | Variable valve driving apparatus |
| US20120199087A1 (en) * | 2011-02-08 | 2012-08-09 | Honda Motor Co., Ltd. | Rocker arm structure |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE673717A (en) * | 1965-01-12 | 1966-06-14 | ||
| US3395689A (en) * | 1966-09-15 | 1968-08-06 | Studebaker Corp | Engine decompression apparatus |
| IT1254606B (en) * | 1992-02-10 | 1995-09-28 | Cagiva Motor | AUTOMATIC DECOMPRESSION DEVICE OF A MOTOR OF A MOTORCYCLE IN THE STARTING PHASE |
| EP1712747A1 (en) | 2005-04-17 | 2006-10-18 | Uwe Eisenbeis | Valve train with variable valve stroke and timing for high-speed engines |
| GB201406661D0 (en) * | 2014-04-14 | 2014-05-28 | Triumph Designs Ltd | Decompression device |
| JP2015224579A (en) * | 2014-05-27 | 2015-12-14 | ヤマハ発動機株式会社 | Engine and vehicle |
| GB201503074D0 (en) * | 2015-02-24 | 2015-04-08 | Triumph Designs Ltd | Decompression device |
-
2016
- 2016-10-07 DE DE102016119105.1A patent/DE102016119105A1/en not_active Ceased
-
2017
- 2017-10-06 BR BR112019006860A patent/BR112019006860A2/en not_active Application Discontinuation
- 2017-10-06 CN CN201780062263.7A patent/CN109952416B/en active Active
- 2017-10-06 EP EP17780420.0A patent/EP3523513B1/en active Active
- 2017-10-06 WO PCT/EP2017/075544 patent/WO2018065602A1/en unknown
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3381676A (en) * | 1967-04-12 | 1968-05-07 | Tecumseh Products Co | Compression relief mechanism |
| US5682847A (en) * | 1995-10-12 | 1997-11-04 | Unisia Jecs Corporation | Valve actuating device for engine |
| EP1247950A2 (en) * | 2001-03-30 | 2002-10-09 | Tecumseh Products Company | Mechanical compression and vacuum release |
| EP1892388A1 (en) * | 2006-08-08 | 2008-02-27 | HONDA MOTOR CO., Ltd. | Engine with decompression device |
| JP2008082188A (en) * | 2006-09-26 | 2008-04-10 | Honda Motor Co Ltd | Valve gear of internal combustion engine |
| US20090301419A1 (en) * | 2008-06-10 | 2009-12-10 | Kawasaki Jukogyo Kabushiki Kaisha | Decompression Mechanism |
| CN102486101A (en) * | 2010-12-06 | 2012-06-06 | 现代自动车株式会社 | Variable valve driving apparatus |
| US20120199087A1 (en) * | 2011-02-08 | 2012-08-09 | Honda Motor Co., Ltd. | Rocker arm structure |
| CN202117726U (en) * | 2011-08-29 | 2012-01-18 | 重庆银钢汽车配件制造有限责任公司 | Camshaft structure |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3523513B1 (en) | 2024-02-21 |
| EP3523513C0 (en) | 2024-02-21 |
| DE102016119105A1 (en) | 2018-04-12 |
| EP3523513A1 (en) | 2019-08-14 |
| WO2018065602A1 (en) | 2018-04-12 |
| BR112019006860A2 (en) | 2019-06-25 |
| CN109952416B (en) | 2021-11-16 |
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