CN1422359A - Automatic valve clearance adjuster - Google Patents
Automatic valve clearance adjuster Download PDFInfo
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- CN1422359A CN1422359A CN01806118A CN01806118A CN1422359A CN 1422359 A CN1422359 A CN 1422359A CN 01806118 A CN01806118 A CN 01806118A CN 01806118 A CN01806118 A CN 01806118A CN 1422359 A CN1422359 A CN 1422359A
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- housing
- helical element
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- thread
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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
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
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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
- F01L2303/00—Manufacturing of components used in valve arrangements
- F01L2303/01—Tools for producing, mounting or adjusting, e.g. some part of the distribution
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
An automatic valve clearance adjuster comprising an internally screw-threaded housing (1); an externally screw-threaded screw member (3) extending within the housing; the screw thread (4) of the screw member (3) having an external form which is complementary to the thread form of the internal thread (2) of the housing and fits therein with a predetermined axial clearance, the thread being trapezoidal in form, symmetrical in axial cross-section and exhibiting equal frictional resistance against movement in both axial directions; wherein the flank angles, helix angle and number of starts of the screw thread are selected to ensure that the screw member will rotate and advance axially out of the housing solely under the influence of an axial force on its end within the housing; and the emerging end (7) of the screw member is adapted to work in conjunction with an adjacent component to receive therefrom a frictional resistance to rotation.
Description
Summary of the invention
The present invention relates to a kind of automatic valve clearance adjuster, this valve clearance regulator can be used in the valve operating gear as internal-combustion engine; This regulator comprises the screw shell of an internal spiral, the outside thread helical member that extends and power bringing device in housing, this power bringing device axial action on helical member and make its rotation and from the opening end of housing outwards motion to prolong regulator; The worm structure that matches of constructing on helical member and the housing helical member is freely rotated and effect at described axial force under the housing that moves out of.
But when in the space between the parts of two relative movement that this valve clearance regulator are placed on valve operating gear, helical member engages with another parts housing with a part bonding, regulator is by extending and by helical element move out of housing and gap in the shrinking valve operating device, the space between its complete collapsible part.By the form of example, regulator directly or indirectly can be inserted between a cam and valve or the valve functional unit.In another kind was arranged, regulator can be level type valve functional unit a fulcrum is provided, and the position of fulcrum changes by the operating clearance that regulator shrinks.
The background technique of the present invention of some examples of comprising prior art and some aspects of the present invention itself are described with the form of example below in conjunction with accompanying drawing, wherein:
Fig. 1,2 and 3 has shown automatic valve clearance adjuster possible deployment scenarios in the valve operating gear of internal-combustion engine;
Figure 4 shows that amplification view according to the screw of regulator of the present invention;
Fig. 5 has shown the schematic representation according to the part of a kind of automatic valve clearance adjuster of the present invention, cam follower and relevant cam position, needs regulator to come gap in the shrinking valve system at described corresponding cam position place;
Fig. 6 has shown that the valve clearance regulator among Fig. 5 reaches the indication to corresponding cam position, and at this corresponding cam position place, regulator has been eliminated the gap in the valve system just;
Fig. 7 has shown the part of valve clearance regulator among Fig. 5 and Fig. 6, cam follower and to a schematically indication of corresponding cam position, at this corresponding cam position place, valve system just in time begins to open a valve;
Fig. 8 has shown an automatic valve clearance adjuster according to prior art, and this valve clearance regulator has been contracted in one or more positions in the engine valve system such as position A, B, C, original already present gap, D place;
Fig. 9 has shown the situation of the regulator among Fig. 8 when valve is opened;
Figure 10 has shown an automatic valve clearance adjuster according to another embodiment of prior art;
Figure 11 has shown the valve clearance regulator shown in Fig. 8 and Fig. 9, and wherein, spiral laterally moves in the housing of regulator;
Figure 12 has shown the regulator shown in Fig. 8 and Fig. 9, and wherein, spiral moves in the housing medium dip;
Figure 13 shows that the partial view of the contact side of coupling screw with a less side angle;
Figure 14 shows that the partial view of the contact side of coupling screw with a larger side angle;
Figure 15 shows that the partial view of the screw of coupling, shown the relation between axial screw thread gap and the radial thread relief among this figure;
Figure 16 shows that residing a kind of state before will regulator according to the present invention being fit into motor;
Figure 17 has shown an automatic valve clearance adjuster according to another aspect of the present invention, and this regulator is prepared to be fit in the motor.
In all claims, corresponding parts are all adopted corresponding reference number.
At first with reference to figure 1,2 and Fig. 3.All shown an automatic valve clearance adjuster among every width of cloth figure in these three accompanying drawings, automatic valve clearance adjuster comprises: housing 1; Extend into the internal spiral threads 2 in the housing; A helical element 3 with external spiral screw thread 4, the external spiral screw thread 4 of this helical element 3 matches with the internal thread 2 of housing.Reference number 5 indication be the axial force that applies to helical element by spring assembly at 6 places, end of helical element, spring assembly is arranged in the housing; This active force is preferably applied by the pressure spring that engages with helical element that hereinafter will describe.What reference number 7 was indicated is the end of helical element, this end is protruding and engage with a co-acting part of valve operating gear from housing 1, so that transmit the valve steering force or a reaction force be provided according to the characteristic of valve operating gear, when being unlocked when resisting the active force of its closing spring under the action of cam of valve on camshaft, the above-mentioned action that reaction force is provided is necessary.
In example shown in Figure 1, regulator be from hold formula and be fixed in the groove in the motor matrix.The valve actuation ends 7 of stretching out of helical element 3 has a hemispheric end and has spherical surface, and described domed ends is engaged in the chamber 9 of cam follower 8.Described chamber 9 has pointed arch or tapered cross-section, thereby has formed and domed ends 7 contacted narrower endless belt.The rotation of cam 10 makes cam follower 8 around the fulcrum vibration that is provided by domed ends 7, thereby comes the actuating engine valve by valve handle 11.
The housing 1 that shows in Fig. 1 has the lower end of an opening, if pressure 5 is provided by oil pressure, the lower end of this opening is very suitable.As described in hereinafter, for the situation that pressure 5 is provided by spring, housing just has a closed end.
With reference to figure 2, shown among the figure to be included in a regulator in " bucket " type cam follower; Housing 1 preferably forms with bucket 13 integral body.The shape of the valve actuation ends 7 of helical element 3 is determined to such an extent that form the contact area of circular, annular or taper with valve handle 14.In this design of valve actuating mechanism, bucket 13 is slidingly mounted in the interior hole of motor matrix.Cam 10 is by bucket 13 direct controls, and like this, regulator just applies downward valve operational movement to valve 14.
In example shown in Figure 3, regulator be from hold formula and with being used as a push rod that can between cam 15 and rocker arm 17, move.Regulator slidably is installed in to property in the hole of motor matrix.Regulator will move and be sent to the rocker arm 17 that can pivot around axis 41 from cam 15, thereby the valve operational movement is applied to valve 18 downwards.Regulator is equipped with a pressure pad 16, and this pressure pad is arranged between the valve actuation ends 7 of rocker arm 17 and helical member 3.Pressure pad can endwisely slip in housing 1, but is limited and can not rotates therein.
Except above-mentioned design form, regulator also can be bonded in the valve system of other type.For example, governor body 1 can be an integrated part of the rocker arm in rocker arm/transfer bar mechanism.
With reference now to Fig. 8,9 and 10 and will prior art be described,, all shown a valve clearance regulator in each accompanying drawing of these three accompanying drawings, this valve clearance regulator helical member in the screw shell that mainly included, just as noted before.Under each situation, the valve clearance regulator has shown that all one type engine valve is the schematic situation of mechanism, has shown the described regulator that is in the work relationship among the figure.The valve that this theory that is proposed may be used on any other is in the mechanism.
In a kind of prior art there are several variations in a kind of working principle, wherein, above-mentioned spiral is not subjected to the effect of axial force, but is driven and the housing that moves out of under the effect of torsion spring.This can make an explanation with reference to Figure 10, and Figure 10 has shown the cam 10 of motor, and the cam among the figure is in position, an angle, this position, angle can make engine valve shown in reference number 39 place's closures.Figure 10 also demonstrates torsion spring 29 and has driven helical member 30, and like this, described helical member has just moved out of housing 38 to eliminate the original already present any gap in one or more positions such as position A, B, C and D place in engine valve system.In addition, Figure 10 demonstrates a continuous path of compressive force, and this path, is passed position A, B, C and D then and arrived the top of motor valve handle 34 by contact screw (for example, 33 places, position shown in the figure) from the pedestal 31 of housing 38.Therefore, the different heat expansion of the different parts of motor can produce a kind of like this state, promptly stops the closure (for example shown in the reference number among Fig. 9 40) of valve, thereby causes the wearing and tearing of parts and reduced the performance of motor.This all is a kind of more serious defectives in all valve clearance regulators, and this situation is to produce under the effect of torsion spring.
The another kind of classification of prior art (GB-A-2033472, EP-T-0032284, GB-2160945, GB-2211263, WO-A1-89/05898, WO-90/10786, WO-90/10787) in, above-mentioned internal thread and outside thread are buttress threads; This feature is the common characteristic of this kind device.Shown this structure in Fig. 8, wherein, the form with axial cross section among the figure has shown helical member 3 and housing 1.With become G with the perpendicular straight line of axis
RThe buttress thread side 24H and the 24S at inclination angle is called " running side ".With become G with the perpendicular straight line of axis
LThe buttress thread side 25H and the 25S at inclination angle is called " locking side ".Helix angle is Z.
Fig. 8 has shown the engine cam 10 that is in position, an angle, and this position, angle can make engine valve 11 close in the position shown in the reference number 39.Also demonstrate among the figure: pressure spring 22 has been pushed into the running side 24S of spiral and has contacted with the running side 24H of housing and helical member 3 is released housings 1 to eliminate one or more positions in engine valve system such as A, B, C and D place already present any gap originally.The motion that helical member 3 comes out from housing is called " contraction " motion hereinafter.
Fig. 9 has shown that engine cam 10 has rotated a kind of state into position, an angle, and wherein, engine cam applies the effect of a power, and the effect of this power is subjected to the reaction of the helical member 3 of valve handle 11 and clearance adjuster.Reaction on the valve handle is at the position open valve shown in the reference number 40; Reaction on the spiral then forces the locking side 25S of spiral to contact with the locking side 25H of housing through gap (shown in the reference number 26 among Fig. 8).In theory, the opposing that is combined in of spiral 3 and housing 1 should be an integral body in the described reaction, this is because should stop helical rotation and along with the contraction that takes place enters housing, the surface friction drag of described raising comes from the relatively large tilt angle G of locking side by the surface friction drag that improves
L
Put it briefly, in theory, the application of buttress thread should guarantee: under the effect of the axial force that applies, to helical member 3 being pressed into there is higher resistance in housing there is lower resistance in the helical member housing that moves out of.
Actual test demonstrates: attempt above-mentioned operating principle is applied to and have multiple difficulty in the reality, described difficulty will be described hereinafter:
Shown in reference number among Fig. 8 26, it is necessary should having certain predetermined axial clearance between screw thread on helical member and the screw thread in the housing, and this gap can guarantee not hinder the closure of valve.For guaranteeing helical member free-running operation in housing, also need have radial clearance, shown in the reference number among Fig. 4 19 in threaded tip and adjacent thread root.Like this, as shown in figure 11, helical member 3 just can laterally move and with respect to housing 1 off-centre, perhaps, as shown in figure 12, helical member 3 can tilt with respect to housing.Be at helical member under the situation of one of above-mentioned these positions, when under the effect of spring 22 with one of the running side of screw and running side of housing screw thread when another promotes, if the bus 35 (referring to Figure 11) on surface of running side is too closely and not perpendicular apart from the line of action of force that spring 22 applies, then to return back to the tendency of concentric position just very little for spiral.Figure 13 and Figure 14 have shown the basic view of this situation.Figure 13 and Figure 14 are the zoomed-in view of the tag slot F among Figure 11 and Figure 12.In example shown in Figure 13, side angle G
RBe to draw with less tilt angle.Figure 14 has shown another example, wherein drawn side angle G
LHas bigger tilt angle.Reference number 36,37 has been indicated the element of the running side 24S of helical member and the running side 24H in the housing respectively.In two examples each all is under the identical friction situation, compares with example shown in Figure 14, and power P more is easy to generate motion Q in example shown in Figure 13.Motion Q is necessary for described helical member in housing 1 again between two parties.
Like this, just as observed in the actual tests, when the tilt angle of running side is low, helical member 3 just may remain in the disadvantageous position in the housing 1, shown in Figure 11 or 12, in these disadvantageous positions, the running side of the screw thread in the running side of the screw thread on the helical member and the housing only contacts as line or the some contact, and the contact (being boundary lubrication condition) of continuous " face is to face " that undertaken by oil film is impossible, so just produced the higher friction resistance, this surface friction drag has stoped the carrying out of " contraction " motion under most of situation.Though to be lubricated be common accepted practice to double thread under from the effect of the pressure of engine lubrication system, but under above-mentioned some contact or line contact situation, can not keep required continuous oil film to lubricate, therefore, friction has stoped the carrying out of " contraction " motion or has made this motion become slow with regard to becoming excessive.
On the contrary, referring to Fig. 9, when valve opening force combined the locking side 25H of the locking side 25S of the screw thread on the helical member and the screw thread in the housing, the angle of locking side was favourable to spiral in housing between two parties.Like this, just can have continuous film lubrication state and can produce helical member 3 at once to enter motion (being called " afterwards returning motion ") in the housing 1, the compressive force that this motion goes between the locking side that acts on joint is always destroyed oil film and is produced intermetallic contact.
Put it briefly, although there is theoretic high friction/low friction performance in locking side/running side, " afterwards returning motion " may be too greatly and/or " contraction " move too little.Close at each valve/opening of valves circulation in, move if " afterwards returning motion " surpasses " contraction ", spiral 3 is with regard in the retraction housing 1 gradually, and is just to lose contact between the parts of mechanism at valve.
Just as above-mentioned content is described,, when utilizing buttress thread, in the manufacturing of screw thread, has difficulties and have the problem of useful life longevity for the defective in the performance.Described these problems are as follows:
In internal thread and externally threaded manufacture process, above-mentioned axial clearance (in Fig. 8 and Fig. 9 respectively by shown in reference number 26 and 9) must be by remaining in the approaching boundary near control.If described gap is too big, the operation of valve will be unsatisfactory and noise is arranged.With reference to figure 8,9 and 15, G
LAnd G
RRepresentative value be respectively 75 ° and 15 °.(KM among Figure 15) represents that with symbol C then axial clearance is with radial clearance:
JK+KL＝(C×tangent?15)+(C×tangent?75)
Be 4 times of C.This just means: for example, in the tolerance on the axial clearance be just need internal thread under the situation of 0.1mm and outside thread on the combined radial tolerance be set to about 0.05mm.It is very difficult reaching this requirement in production in enormous quantities.
In use, there is a kind of similar situation in the wearing and tearing for thread surface.Increase four times of distance because the less increase of the caused radial clearance of planarization of surface etching or the surface roughness on inclined side will make axial clearance increase institute, and cause valve unsafty and that have a noise to be operated.
The groove on the locking side of spiral and the layout of ridge in GB-2211263, have been disclosed.This change of introducing in design is to attempt " afterwards to return motion " to remain in the acceptable scope; The wish of design is: the ridge with the surface area that reduces can more easily damage the oil film between the locking side of joint and earlier enter metal and the contacted state of metal, has so just reduced the amplitude that " afterwards returning " moves.Also there are some following shortcomings in this design:
A. have described groove and ridge the locking side manufacturing relatively the difficulty.
B. because the reducing of area of contact, the speed of the wearing and tearing of carrying out on the locking side that engages just increases, and causes the increase of axial clearance thereupon, just as the content of front is described.
The less radial tolerance of (promptly on helical member and in the housing) need be utilized littler tolerance on the screw thread of regulator parts in the manufacturing of instrument, and described littler tolerance is to use in the manufacturing of described parts.This situation is specially adapted to form screw thread on plug screw, described plug screw forms internal thread in housing.In addition, it is wide unusually that partially the trapezoid cross section part requires the tooth of plug screw, can cause like this not wish the high tapping moment of torsion that produces.
The efficient that has a motor of automatic valve clearance adjuster for increase focuses in the friction between the contact surface that reduces cam 10 and cam follower 8.
An object of the present invention is to provide a kind of improvement structure of mechanical valve clearance adjuster, particularly:
A. improve the reliability of " contraction " motion;
B. reduce the friction between cam and the cam follower;
C. avoid producing the ratio of undesirable radial clearance/axial clearance, when described screw thread has an inclined to one side trapezium structure, just between internal thread that cooperates and outside thread, produce undesirable ratio, so just the machining tolerance that needs are very little and also can cause the rapid increase of the axial clearance between the screw thread of cooperation.
Valve clearance regulator according to one aspect of the invention comprises a housing with internal thread, be furnished with one and have externally threaded helical element in described housing, this externally threaded form is usually complementary and be matched with wherein with the axial clearance of being scheduled to the form of the internal thread of housing; Described screw thread be irregular form and in axial cross section symmetry and the motion axially applied same surface friction drag; The side angle of screw, helix angle and initial number are predetermined to guarantee that helical element is can rotate individually under the influence of the axial force that applies on its non-exposed ends and axial motion goes out housing; The adjacent component that the exposed ends of described spiral is configured to the valve of for example IC motor be combines to absorb the surface friction drag that stops rotation from described adjacent component; The non-exposed ends of described spiral is constructed like this, promptly works as it and is subjected to the time spent of doing of above-mentioned axial force, and this non-exposed ends can assist helical element to carry out axial motion.
A possible reason of " contraction " bradykinesia is: as Figure 11 and shown in Figure 12, spiral 3 has motion and goes into the trend with housing 1 decentraction position.In the present invention, by increasing the tilt angle G of the running side of discussing according to Figure 13 and 14
RReduce this trend.
For avoiding requiring to have very little tolerance on the diameter of screw, people wish obviously to reduce following ratio: just as having discussed with reference to Figure 15:
Axial clearance ÷ radial clearance=tangent G
L+ tangent G
R
Adopt such example, i.e. a G now
RIncrease to 30 ° from 15 °, and G
LFrom G
L=75 ° are decreased to 30 °, and described ratio is that axial clearance ÷ radial clearance is reduced to (30 ° of 2 * tangent) from (75 ° of 15 °+tangent of tangent) and promptly, is decreased to 1.15 from 4.
Like this, in the present invention, when in axial cross section, observing, on the threaded part and the side of each screw thread in the housing be preferably in perpendicular each side of the axis of screw on 30 ° angle tilt.These side angles find in modern screw thread, and described modern screw thread is used in the bolt of standard and nut etc., and is referred to as 60 ° of screw threads.This screw thread has such advantage and is the check purpose, can use common conventional device, and for example: microscope lattice, screw measurement pin, screw measurement apparatus, slit instrument and optical emission instrument detect.
Therefore, the angle G of running side
REqual the angle G of locking side
L, that is, and G=G
R=G
L=30 °.Suppose helix angle to represent with symbols Z and friction factor is represented with symbol μ, spiral rotates under the effect of axial load and the state that moves is provided by following formula:
tangent?Z＞μ÷cosine?G
This formula hypothesis friction on the spiral end is insignificant, and described end absorbs axial force.As approaching example, if external diameter is 8mm and first screw thread be the friction co-efficient value of spiral of 4mm less than 0.14, then it will rotate under the effect of axial load and advance.Described first screw thread increase for can utilizing higher friction factor, 5mm promptly 0.17 is realized gratifying operation.The two start screw threads of utilization just can realize the designing shape according to the screw of these examples satisfactorily.
So just can have a helical element, it is 30 ° symmetrical screw thread that this helical element has side angle G, this helical element axial rotation and advancing alone under the effect of axial force.In addition, 30 ° side angle can make helical element keep with one heart with respect to housing, and has just avoided the some contact condition that produces when utilizing less side angle like that as previously described.Like this, under the effect of axial force, just can realize " contraction " motion.This axial force can provide by the oil pressure that for example comes from engine lubrication system or be provided by a small-sized spring assembly, and this spring assembly preferably affacts on the end of spiral by the medium of pommel plunger.
Actual test demonstrates: when helical element being made as " V " shape form of symmetry, described helical element just can produce enough big resistance to " afterwards returning " motion by providing the external friction moment of torsion in the spiral end, and this end contacts with coefficient parts of engine valve system.
According to the designing shape of engine valve system, the contact area of the acting in conjunction parts of the end of helical element and valve system can be following form, for example:
A. loop wire
B. annular region
C. approach the zone of the curved surface of frustum
D. the zone of the curved surface of the slice of spheroid.
Under the situation of b, c or d, the width dimensions of contact area can be enough little of to prove such hypothesis: promptly contacting situation is the Line of contact of a circle.In all cases, all to rotate the axis that is centered on consistent with helical element with the axis of the perpendicular circle of disk.All can set a value D and represent diameter of a circle in each of four examples, surface friction drag and this circle are tangent.Suppose that the average diameter of screw represents with symbol d, the external friction resistance of " afterwards returning " motion is mainly depended on the ratio of D ÷ d, like this, described external friction resistance can be controlled by the design to following part:
I. the average diameter of spiral
II. the valve actuation ends of helical element
III. the part of the parts of valve system, this part contacts with helical element.
By the form of example, engine test demonstrates: when being 10 ° screw when utilizing the ratio of D ÷ d=2 in conjunction with having helix angle, just can move to regulator " afterwards returning " and carry out enough control.Can carry out reliable so again and corresponding " contraction " motion.
5A, 6,6A, 7 and 7A and utilize with the corresponding example of Fig. 1 and will the operating mode according to regulator of the present invention be described now, with reference to the accompanying drawings 5.Fig. 5 has shown when the gap between the engine valve based part has been developed that helical element 3 is the position in the residing imagination in housing 1.Describe for simplifying, the total amount in the gap shown in the figure is the end 7 of helical element 3 and the gap 42 between the chamber 9 in the cam follower 8.In this state, cam 10 can be in any angular orientation, and wherein, its constant radius part contacts with cam follower 8, has schematically shown this situation among Fig. 5 A.Owing to have bigger helix angle and lower friction torque resistance between the bulb-shaped recess in the end 6 of ball 29 and helical element, therefore, spring 22 can produce " contraction " motion, the surface in the chamber 9 of the housing 1 even helical element 3 moves out (shown in the figure for upwards) in pommel 7 and cam follower 8 contacts, as shown in Figure 6.
For state shown in Figure 6, should note 3 points:
A) cam 10 still can be in position, any angle, and wherein, any point on its constant radius part all contacts with cam follower 8, just as Fig. 6 A schematically shows ground.
B) (as shown in the figure) maintains gap 43 below the screw thread of helical element 3, and just situation as shown in FIG. 5 is the same.
C) power that is applied by the surface in the chamber 9 in the 7 pairs of cam followers 8 in pommel is less.The power that described power is restricted in the spring 22 deducts to producing the required power of " contraction " motion.
Fig. 7 and 7A have shown a kind of like this state, and wherein, cam 10 has changed a position over to, in this position, and its just in time enough actuating cam follower 8 and helical element 3 is moved downward and through unborn gap 43.That is to say: described gap is on the screw thread of helical element 3 (shown in the reference number 44) at present.At this moment, have continuous oil film between the screw thread of cooperation, therefore, 1 pair of helical element 3 of housing " afterwards returning " of making progress motion has very low resistance.Therefore, the resistance to " afterwards returning " motion is to be provided from the outside by friction by the contacting part between the surface in the end 7 of helical element and the chamber 9 in the cam follower 8.
Subsequently, cam 10 rotates a little and the load of whole valve system is increased rapidly, to overcome engine valve is remained on power required on its position.Above-mentioned oil film between the matching thread is destroyed, and the friction at screw thread place produces an internal drag to " afterwards returning " motion.
Under the situation of given thread construction geometry and friction condition, above-mentioned external drag to " afterwards returning " motion mainly depends on ratio D ÷ d, wherein:
The effective diameter of the rubbing contact circle of D=between the surface in the end 7 of spiral and the chamber 9 in the cam follower 8.
The average diameter of d=screw.
Just can obtain required resistance by designing following part like this to " afterwards returning " motion:
I. screw (being its effective diameter)
II. the valve actuation ends 7 of helical element 3
III. valve is fastened the end 7 contacted parts parts with helical element 3.
In addition, by increasing angle W (referring to Fig. 6) i.e. angle between the common tangential of the contact surface in cross-table and chamber 9 and pommel 7, can obtain the resistance of increase that " afterwards returning " moved.
Engine valve is opened in the further rotation of cam 10, then it is closed, and valve system is returned back to and Fig. 5 or the corresponding state of Fig. 6.
When automatic valve clearance adjuster according to the present invention is not packed valve operating gear into, when promptly not being assembled in it in motor, it just is not subjected to the constraint of the parts that it is engaged in mechanism, the power bringing device can make the helical element housing that moves out of to the full extent.In this case, regulator just can not be assembled in the motor, so just need be set back in the housing with relative rotation regulator is shortened, enough be reduced to until the whole length of regulator and can place it between the corresponding parts by helical element.In the relevant position in each parts that a plurality of this regulators are assembled into the engine valve operating device with a plurality of valves, some devices of significant need are temporarily to be kept at regulator in the position of its retraction, so that this assembling becomes easy.
A wide in range purpose of another aspect of the present invention is to satisfy above-mentioned requirements so that regulator is kept in the position of its retraction.
Therefore, according to another aspect of the present invention.I provide a kind of valve clearance regulator, and this valve clearance regulator comprises: the housing with internal spiral threads; Extend into a helical element the housing from the opening end of housing, this helical element have with housing in the external spiral screw thread of engage threads; On the Y of helical element to its spring assembly that works.The screw thread of the operation that matches of helical element in this structure and housing can make helical element rotate and move out housing under the effect of spring assembly; Wherein, arranged device in this valve clearance regulator in abutting connection with (abutment), when interior location helical element being screwed in the housing, this abutment means can be moved between helical element and housing, thereby, between helical element, housing and abutment means, produce enough frictional force and helical element remained in the described interior location with the active force of antagonistic spring device.
In a kind of valve clearance regulator aspect this according to the present invention, helical element can be screwed in the interior location in the housing, and matches with the abutment means that can move between helical element and housing in this position.Then, if helical element tightened and between helical element, abutment means and housing, apply the active force of an increase, then will produce the effect of enough big frictional force with the antagonistic spring device between them, the effect of spring assembly is to make the helical element housing that moves out of.The size of valve clearance regulator should be determined, and like this, when helical element was in its interior location, the overall length of regulator was enough little of on the desired location in the operating device that it easily can be assembled in engine valve; So just can easily assemble motor with a plurality of valve clearance regulators.Test demonstrates: when ato unit, by the impact of the cam that is used for handling particular usage valve and can eliminate friction lock between helical element and housing completely in the vibration that each regulator produces, like this, helical element just can occupy the correct working position with respect to the housing of regulator immediately.
The helical element of regulator can engage by an instrument, helical element can be screwed into by this instrument to make abutment means enter foregoing running state in the housing.Among the regulator embodiment hereinafter, helical element has an end, this end have part for spherical surface with rocker arm or analog in an auxiliary part be sphere groove engages, the instrument that engages with helical element can comprise a groove or be called depression, the surface structure that this groove or depression have can carry out frictional engagement and it is tightened with the end of helical element, thereby when helical element is in its interior location, helical element is engaged with abutment means.
Abutment means can comprise a shoulder that is arranged in enclosure interior, and when helical element was in its interior location, this shoulder can engage with the inner terminal face of helical element.This shoulder can be provided by housing itself, or can by one independently parts provide, provide the individual components of this shoulder can be inserted in the housing as a cover.
Another kind of mode is: helical element can be furnished with one and stride junction structure, and this is striden junction structure and can engage with the end face of housing.This structure can comprise a band of column that is arranged on the helical element, and this band of column is positioned at below the end of helical element.When the band of column engaged with housing, the described band of column also can be used for keeping helical element to tighten so that it is screwed in the housing and with it, and for a kind of independently instrument of using in this case, this band of column not necessarily.
Preferred situation is: this valve clearance regulator is made according to a first aspect of the invention.But this regulator also can be a kind of regulator that combines as with buttress thread of the prior art recited above.
Shown a kind of regulator shown in Fig. 5,6 and 7 among Figure 16, can suppose that in this case this regulator is not assembled in the motor.The helical element housing that moved out of, like this, the overall length of regulator will be significantly greater than by regulator occupied space in motor.
Therefore, for regulator is assembled in the motor, helical element 3 must be screwed in the housing 1 to a certain degree and the overall length of regulator is decreased to certain size with easy assembling.This overall length of regulator will be slightly less than the typical running length of the regulator shown in Fig. 6 and Fig. 7.
If the feature of the screw of operating between helical element and governor body is such, be that helical element can not remain in the position by friction, then be in similar to position shown in Figure 5 one during interior position when helical element, between helical element and housing, arrange the abutment means that to move according to the present invention.A kind of form of this abutment means as shown in figure 17, the abutment means that provides by pipe box 50 be arranged in housing and the spring 22 that surrounded between.One end of pipe box 50 leans against on the closed lower end 51 of housing, and its other end leans against on the end face 6 of helical element and be in wherein in the annular region of a groove.
When helical element being screwed in the housing and with adjacency pipe box 50 be right after fashionable, between helical element and pipe box, just produced the effect of power, although spring 22 also applies the effect of power to helical element, the threads engaged between helical element and the housing and with the helical element frictional property remain on interior position.Regulator is more easily assembled.But when startup wherein was equipped with the motor of regulator, the impact of cam can be eliminated the friction lock between helical element and the housing completely, and like this, spiral just can occupy above-mentioned suitable working position immediately.
Replace pipe box 50, housing can arrange that an integrated type strides junction structure, can stride junction structure with this during interior position and engages when helical element is in it.This structure can be passed through: for example, under the internal spiral threads lower end and the spring 22 that occupies the smaller diameter portion in the housing provide.Another kind of possible situation is: can arrange that under the end of helical element the band of column is to engage with the exterior edge face 55 of housing outside one.When helical element is screwed in the housing when the band of column leans against on the housing, this band of column can be used as the device that is used to rotate helical element.
If helical element do not arrange a kind of like this band of column or by this way helical element is screwed into other structures in the housing, can utilize as the 52 indicated a kind of instruments of the reference number among Figure 17 to engage with the end 7 for the part sphere of helical element with its rotation.Instrument 52 has a cone tank 53, angle at cone tank 53 1 ends is to arrange like this, promptly when this end that makes cone tank with hand instrument 52 engages with the end of helical element, cone tank will be with the end of enough big power friction clamping helical element the active force of antagonistic spring 22 so that helical element is screwed in the housing, thereby engage with adjacency pipe box 50.Instrument 52 has a grip portions 54, and this grip portions 54 can be gripped and easily with its rotation by the people who uses this device.
As mentioned above, in some designs that combine with spring assembly with the regulator that helical element moved axially out housing, can not be the above-mentioned convenient assembling of regulator in motor that need simplify.Just as the reference of top institute, Engine Block Test demonstrates: to utilize D/d be 2 ratio and be that 10 ° screw just can carry out enough control to " afterwards returning " motion of regulator in conjunction with helix angle, thus produce the reliable of regulator and corresponding " contractions " move.But, under the situation that the general arrangement of considering motor limits, just have to consider lower D/d value and lower thread helix angle.For example, helix angle that is had is 6 ° a regulator, when it is subjected to enough when lubricated in motor, it should produce enough " contraction " motions, and should have enough screw thread frictions and do not need the device assembled helical element is remained in the interior location in the housing.
In the application's narration, " comprising " mean " contain or by ... constitute ", and " comprising (comprising) " be meant " contain or by ... constitute (including or consistingof) ".
Disclosed feature of the present invention with specific forms in the content in front or in following claim or in the accompanying drawings, the disclosed device of the present invention is carried out disclosed function, foregoing has also disclosed a kind of method or process that realizes described result, and these features can be independently or the form of combination and realize the present invention with different forms.
Claims (23)
1. an automatic valve clearance adjuster comprises: the housing (1) with internal thread; A helical element that has outside thread and in housing, extend (3); The screw (4) of helical element (3) has the external thread form with the thread forms complementation of the internal thread (2) of housing, and the two matches with predetermined axial clearance, described screw thread be trapeziform form and in axial cross section symmetry and the motion axially applied identical surface friction drag; Wherein: the side angle of screw, helix angle and initial number thereof are can rotate individually under the effect with the axial force that guarantees to apply on helical element its end in housing through selecting and axial motion goes out housing; The exposed ends of described spiral (7) combines with an adjacent component and stop the surface friction drag that rotates to absorb from described adjacent component.
2. automatic valve clearance adjuster according to claim 1 is characterized in that: on the helical element and the side of each screw thread in the housing with respect to the straight line of the axis normal of screw with 30 ° of angle tilts.
3. regulator according to claim 1 and 2 is characterized in that: the exposed ends of helical element is used for contacting with the described adjacent component of one of following part:
(a) loop wire
(b) annular region
(c) the curved surface zone of thin frustum
(d) zone of the curved surface of the slice of spheroid.
4. regulator according to claim 3 is characterized in that: with b, c or d in the contacted situation of described adjacent component under, contact area is approximately linear contact.
5. according to claim 3 or 4 described regulators, it is characterized in that: the diameter in described Line of contact or zone is greater than the average diameter of the screw in the regulator.
6. according to the described regulator of arbitrary claim in the aforementioned claim, comprise spring assembly, this spring assembly acts on the helical element to force its axial motion to go out described housing.
7. regulator according to claim 6 is characterized in that; Described spring assembly acts on the end of the helical element in the housing by the parts with pommel.
8. according to the described regulator of arbitrary claim in the claim 1 to 5, it is characterized in that: described helical element is subjected to the effect of oil pressure and forces its axial motion to go out described housing.
9. according to claim 6 or 7 described regulators, it is characterized in that: arrange abutment means, when helical element being screwed in the housing to an interior location, abutment means can be moved between helical element and housing, helical element is remained in the described interior location with the active force of antagonistic spring device thereby produce enough big frictional force between helical element, housing and abutment means.
10. a valve clearance regulator comprises: the housing with internal spiral threads; Extend into one of them helical element from an opening end of housing, this helical element has the external spiral screw thread that engages with spiral in the housing; Spring assembly, this spring assembly acts on the helical element on its longitudinal axis; The screw of helical element and housing matches, and this structure is rotated and the housing that moves out of helical element under the effect of spring assembly; Wherein: arrange abutment means, when helical element being screwed in the housing to an interior location, abutment means can be moved between helical element and housing, helical element is remained in the described interior location with the active force of antagonistic spring device thereby produce enough big frictional force between helical element, housing and abutment means.
11. according to claim 9 or 10 described regulators, it is characterized in that: described abutment means comprises a shoulder that is in the housing, and this shoulder can be engaged by an inner terminal face of helical element.
12. regulator according to claim 11 is characterized in that: described shoulder is provided by housing.
13. regulator according to claim 11 is characterized in that: described shoulder is provided by parts that are arranged in the housing.
14. according to claim 9 or 10 described regulators, it is characterized in that: described helical element has an abutment structure that can engage with an end face of housing.
15. regulator according to claim 14 is characterized in that: described abutment structure comprises and is arranged on the helical element and is in the band of column under its end.
16. regulator according to claim 15 is characterized in that: the described band of column is used for keeping helical element so that it is screwed into housing.
17. according to the described regulator of arbitrary claim in the claim 9 to 16, it is characterized in that: helical element is fit to be engaged so that it is screwed in the housing by an instrument, and makes described abutment means be in running state.
18. the combination of regulator according to claim 17 and the described instrument that engages.
19. combination according to claim 18 is characterized in that: the end frictional engagement of described instrument and helical element.
20. include a kind of valve operating gear according to the described automatic valve clearance adjuster of arbitrary claim in the claim 1 to 17, this operating device is arranged between the corresponding parts of mechanism to shrink gap therebetween.
21. include a kind of internal-combustion engine of a plurality of valve operating gears according to claim 20.
22. Fig. 5 to 7 or 17 and press the described a kind of automatic valve clearance adjuster of foregoing basically in reference to the accompanying drawings.
23. the shown any novel characteristics or the combination of novel feature in described herein and/or the accompanying drawing.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0003300.1 | 2000-02-02 | ||
| GB0003300A GB0003300D0 (en) | 2000-02-02 | 2000-02-02 | Automatic valve clearance adjuster |
| GB0026081.0 | 2000-10-25 | ||
| GB0026081A GB2368370B (en) | 2000-10-25 | 2000-10-25 | Automatic valve clearance adjuster |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1422359A true CN1422359A (en) | 2003-06-04 |
Family
ID=26243642
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN01806118A Pending CN1422359A (en) | 2000-02-02 | 2001-01-31 | Automatic valve clearance adjuster |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US20030075131A1 (en) |
| EP (1) | EP1252418A2 (en) |
| JP (1) | JP2003521624A (en) |
| KR (1) | KR20030041853A (en) |
| CN (1) | CN1422359A (en) |
| AU (1) | AU2001230386A1 (en) |
| BR (1) | BR0108072A (en) |
| CA (1) | CA2399059A1 (en) |
| MX (1) | MXPA02007401A (en) |
| WO (1) | WO2001057367A2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101305167B (en) * | 2005-11-12 | 2010-12-08 | 谢夫勒科技有限两合公司 | Method for the variable valve actuation of an internal combustion engine |
| CN102330581A (en) * | 2010-07-12 | 2012-01-25 | 谢夫勒科技有限两合公司 | Mechanical valve clearance compensation element with two-part adjusting bolts |
| CN103703220A (en) * | 2012-03-16 | 2014-04-02 | 日锻汽门株式会社 | Mechanical lash adjuster |
| CN103993923A (en) * | 2013-02-15 | 2014-08-20 | 欧德克斯有限公司 | Lash adjuster |
| CN104895632A (en) * | 2015-04-16 | 2015-09-09 | 奇瑞汽车股份有限公司 | Roller rocking arm air valve mechanism with mechanically adjustable air valve gap |
| CN108026808A (en) * | 2016-06-17 | 2018-05-11 | 日锻汽门株式会社 | Valve mechanism and mechanical slack adjuster |
| CN108952872A (en) * | 2017-05-19 | 2018-12-07 | 卡特彼勒公司 | Public rocker arm for hydraulic lash adjuster and non-hydraulic clearance adjuster |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4155836B2 (en) * | 2003-02-10 | 2008-09-24 | 日産自動車株式会社 | Rush adjuster in valve gear |
| JP2004346821A (en) * | 2003-05-22 | 2004-12-09 | Ntn Corp | Arm type valve gear |
| JP4726775B2 (en) * | 2006-12-20 | 2011-07-20 | ヤマハ発動機株式会社 | Continuously variable valve gear for engine |
| JP2008267224A (en) * | 2007-04-18 | 2008-11-06 | Ntn Corp | Lash adjuster |
| JP4999539B2 (en) * | 2007-05-14 | 2012-08-15 | Ｎｔｎ株式会社 | Rush adjuster in swing arm type valve gear |
| US20100263613A1 (en) * | 2007-12-07 | 2010-10-21 | Makoto Yasui | Lash adjuster |
| WO2009072481A1 (en) * | 2007-12-07 | 2009-06-11 | Ntn Corporation | Lash adjuster |
| JP2009197791A (en) * | 2008-01-22 | 2009-09-03 | Ntn Corp | Lash adjuster |
| JP2009203975A (en) * | 2008-01-28 | 2009-09-10 | Ntn Corp | Lash adjuster |
| JP2009174488A (en) * | 2008-01-28 | 2009-08-06 | Ntn Corp | Lash adjuster |
| JP2009243465A (en) * | 2008-03-10 | 2009-10-22 | Ntn Corp | Lash adjuster |
| US20110036314A1 (en) * | 2008-03-24 | 2011-02-17 | Makoto Yasui | Lash adjuster |
| JP2010007659A (en) * | 2008-05-30 | 2010-01-14 | Ntn Corp | Lash adjuster |
| JP2010019156A (en) * | 2008-07-10 | 2010-01-28 | Ntn Corp | Lash adjuster |
| JP2011127533A (en) * | 2009-12-18 | 2011-06-30 | Ntn Corp | Arm type valve gear |
Family Cites Families (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3118322A (en) * | 1964-01-21 | Figure | ||
| US571067A (en) * | 1896-11-10 | Axle-nut lock | ||
| US2308858A (en) * | 1940-03-04 | 1943-01-19 | Thompson Prod Inc | Hydromechanical clearance regulator |
| US2872961A (en) * | 1954-06-30 | 1959-02-10 | Elastic Stop Nut Corp | Fastening device with means for sealing against both a threaded companion fastener and a worksurface |
| US3024775A (en) * | 1960-04-29 | 1962-03-13 | Wuest Clemens | Valve tappet |
| US3794092A (en) * | 1970-11-23 | 1974-02-26 | Textron Inc | Locking fastener |
| GB1552786A (en) * | 1977-09-26 | 1979-09-19 | Girling Ltd | Clearance adjusters |
| GB2033472B (en) | 1978-08-17 | 1982-11-17 | Gkn Fasteners Ltd | Automatically adjusting valve clearance |
| EP0032284B1 (en) * | 1980-01-12 | 1984-08-29 | Gkn Technology Limited | Valve clearance adjuster |
| GB2160945B (en) | 1984-06-27 | 1988-05-18 | Gkn Technology Ltd | Automatic valve clearance adjuster |
| CH665152A5 (en) * | 1985-01-10 | 1988-04-29 | Urs Kellner | METHOD FOR PRODUCING A CONICAL EXTERNAL THREAD. |
| US4776229A (en) * | 1986-09-19 | 1988-10-11 | D. E. A. Digital Electronic Automation S.P.A. | Device for controlling the rectilinear translation of a movable member |
| JPS63268904A (en) * | 1987-04-24 | 1988-11-07 | Fuji Heavy Ind Ltd | Adjusting method of valve clearance in valve system |
| GB8729660D0 (en) | 1987-12-19 | 1988-02-03 | Gkn Technology Ltd | Automatic clearance adjuster |
| DE3808125A1 (en) * | 1988-03-11 | 1989-11-23 | Man Nutzfahrzeuge Ag | THREADED INSERT WITH A SMALL EXTERNAL DIAMETER FOR SCREWS WITH KEYSTONE THREAD |
| GB8905592D0 (en) | 1989-03-10 | 1989-04-19 | Gkn Technology Ltd | Automatic length adjuster |
| GB8905591D0 (en) | 1989-03-10 | 1989-04-19 | Gkn Technology Ltd | Automatic length adjuster |
| US5078562A (en) * | 1991-05-13 | 1992-01-07 | Abbott-Interfast Corporation | Self-locking threaded fastening arrangement |
| US6032630A (en) * | 1997-11-17 | 2000-03-07 | Ntn Corporation | Valve lifter |
-
2001
- 2001-01-31 EP EP01902531A patent/EP1252418A2/en not_active Withdrawn
- 2001-01-31 US US10/182,888 patent/US20030075131A1/en not_active Abandoned
- 2001-01-31 MX MXPA02007401A patent/MXPA02007401A/en unknown
- 2001-01-31 AU AU2001230386A patent/AU2001230386A1/en not_active Abandoned
- 2001-01-31 JP JP2001555986A patent/JP2003521624A/en active Pending
- 2001-01-31 CN CN01806118A patent/CN1422359A/en active Pending
- 2001-01-31 BR BR0108072-5A patent/BR0108072A/en not_active IP Right Cessation
- 2001-01-31 KR KR1020027009951A patent/KR20030041853A/en not_active Application Discontinuation
- 2001-01-31 WO PCT/GB2001/000410 patent/WO2001057367A2/en not_active Application Discontinuation
- 2001-01-31 CA CA002399059A patent/CA2399059A1/en not_active Abandoned
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101305167B (en) * | 2005-11-12 | 2010-12-08 | 谢夫勒科技有限两合公司 | Method for the variable valve actuation of an internal combustion engine |
| CN102330581A (en) * | 2010-07-12 | 2012-01-25 | 谢夫勒科技有限两合公司 | Mechanical valve clearance compensation element with two-part adjusting bolts |
| CN102330581B (en) * | 2010-07-12 | 2015-11-25 | 舍弗勒技术股份两合公司 | With the mechanical valve clearance compensation element being divided into two-part adjusting bolt |
| CN103703220A (en) * | 2012-03-16 | 2014-04-02 | 日锻汽门株式会社 | Mechanical lash adjuster |
| CN103993923A (en) * | 2013-02-15 | 2014-08-20 | 欧德克斯有限公司 | Lash adjuster |
| CN103993923B (en) * | 2013-02-15 | 2017-07-21 | 欧德克斯有限公司 | Lash adjuster |
| CN104895632A (en) * | 2015-04-16 | 2015-09-09 | 奇瑞汽车股份有限公司 | Roller rocking arm air valve mechanism with mechanically adjustable air valve gap |
| CN108026808A (en) * | 2016-06-17 | 2018-05-11 | 日锻汽门株式会社 | Valve mechanism and mechanical slack adjuster |
| CN108026808B (en) * | 2016-06-17 | 2021-04-27 | 日锻汽门株式会社 | Valve mechanism and mechanical lash adjuster |
| CN108952872A (en) * | 2017-05-19 | 2018-12-07 | 卡特彼勒公司 | Public rocker arm for hydraulic lash adjuster and non-hydraulic clearance adjuster |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20030041853A (en) | 2003-05-27 |
| JP2003521624A (en) | 2003-07-15 |
| BR0108072A (en) | 2004-01-06 |
| WO2001057367A2 (en) | 2001-08-09 |
| AU2001230386A1 (en) | 2001-08-14 |
| WO2001057367A3 (en) | 2002-03-14 |
| CA2399059A1 (en) | 2001-08-09 |
| MXPA02007401A (en) | 2004-09-10 |
| US20030075131A1 (en) | 2003-04-24 |
| EP1252418A2 (en) | 2002-10-30 |
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