CN100393987C - Air valve driver for IC engine - Google Patents
Air valve driver for IC engine Download PDFInfo
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- CN100393987C CN100393987C CNB2003101214387A CN200310121438A CN100393987C CN 100393987 C CN100393987 C CN 100393987C CN B2003101214387 A CNB2003101214387 A CN B2003101214387A CN 200310121438 A CN200310121438 A CN 200310121438A CN 100393987 C CN100393987 C CN 100393987C
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Abstract
SOLUTION: A mechanism has a first rocker arm 5, a second rocker arm 7 and the third rocker arm 6, and switches a driving cam for opening-closing an intake valve and a second intake valve by supply/ release of pressure oil. A third roller follower 24 of the third rocker arm 6 is formed of a double ring-shaped sliding roller structure of an inner roller 22 and an outer roller 23. Impact strength is improved: the rigidity of the abutting part of the third rocker arm 6 to the rotating second low lift cam is improved; the rotation resistance is reduced; friction is reduced by forming a second roller follower 27 to a high lift cam 20 out of a needle bearing; and the rotational resistance is reduced.
Description
Technical field
The present invention relates to and to open and close the valve actuator that ground drives the internal-combustion engine of the intake valve of internal-combustion engine or exhaust valve with different driving timing.
Background technique
In recent years, developed a kind of load condition or speed state according to motor, the performance characteristic of switching the intake valve be arranged in the reciprocating internal combustion engine (motor) or exhaust valve (engine valve) in the best way promptly, open and close regularly or the valve actuator of operating period.
In this valve actuator, a kind of as the mechanism of switch operating characteristic, for example developed rotation status according to motor, use the low speed have the cam profile when being suitable for the low engine speed rotation with cam with have the high speed cam of the cam profile when being suitable for the high engine speeds rotation selectively, make and carry out the technology that engine valve moves with opening and closing.
For example, in patent documentation 1, patent documentation 2, disclosed a kind of like this technology, it has by the driving rocking arm of low speed with cam swing and driving internal combustion engine valve; With the high speed rocker arm of swinging with cam by means of high speed with the cam profile that comprises low speed usefulness cam; And be used to switch the switching mechanism that is connected of the coupled condition that drives rocking arm and high speed rocker arm and off state.
Patent documentation 1: the spy opens clear 63-170513 communique;
Patent documentation 2: the spy opens the 2001-41017 communique.
In the prior art, when making driving rocking arm and high speed rocker arm be in off state by means of the connection switching mechanism, high speed rocker arm is freely swung, and drives rocking arm and swings with cam by low speed, with corresponding to the characteristic of low speed, make the engine valve action with the cam profile of cam.
On the other hand, when making driving rocking arm and high speed rocker arm be in coupled condition by means of the connection switching mechanism, high speed rocker arm is swung with driving the rocking arm one, and the driving rocking arm makes the engine valve action with corresponding to the characteristic of high speed with the cam profile of cam.
In valve actuator in the past, when driving rocking arm and be in coupled condition with high speed rocker arm and internal combustion engine valve is moved, comprise the cam profile of low speed owing to have with cam at a high speed, so the lifting capacity of using cam at a high speed is greater than the lifting capacity of low speed with cam with cam.Therefore, between low speed is with cam and driving rocking arm, turn round under the state in generation gap.
All the time be offset to the cam side owing to drive rocking arm and high speed rocker arm, therefore, under this state, when making driving rocking arm and high speed rocker arm be in off state by connecting switching mechanism, for example, owing to when maximum lift, drive rocking arm and low speed gap maximum, hit the possibility of low speed with the state of cam so existence driving rocking arm is in to kowtow with cam.Thereby its present situation is must consider to drive rocking arm with respect to the rigidity of the low speed that rotates with the structure of the abutment of cam.
Summary of the invention
The present invention proposes in view of above-mentioned condition, its objective is that providing a kind of can make with respect to the rigidity of the support part of the abutment of the rocking arm of rotating cam and the resistance valve actuator for best internal-combustion engine.
In order to finish above-mentioned purpose,
The valve actuator of internal-combustion engine of the present invention comprises: pitman arm shaft; The top is connected with first intake valve or first exhaust valve, can be supported on the above-mentioned pitman arm shaft, by first rocking arm of the first low lift cam driving with freely swinging; The top is connected with second intake valve or second exhaust valve, can be supported on the above-mentioned pitman arm shaft, by three rocking arm of lifting capacity less than the second low lift cam driving of the above-mentioned first low lift cam with freely swinging; Be provided with the top that can be connected, can be supported on the above-mentioned pitman arm shaft with freely swinging, by second rocking arm of lifting capacity greater than the high lift cam driving of the above-mentioned first low lift cam with the above-mentioned first rocking arm side; Be arranged on the terminal side of above-mentioned first rocking arm, hang down first roller follower that lift cam is abutted against with above-mentioned first of camshaft; Be arranged on the terminal side of above-mentioned the 3rd rocking arm, hang down the three rollers driven member that lift cam is abutted against with second of above-mentioned camshaft; Be arranged on the terminal side of above-mentioned second rocking arm, second roller follower that is abutted against with the above-mentioned high lift cam of above-mentioned camshaft; And be used to switch the be connected switching mechanism of above-mentioned second rocking arm with respect to coupled condition with the off state of above-mentioned first rocking arm and the 3rd rocking arm, above-mentioned at least second roller follower in above-mentioned first roller follower and above-mentioned second roller follower forms as the needle roller roller that uses needle bearing, above-mentioned three rollers driven member forms as double-ring slip roller, if hang down below half of interval of lift cam and above-mentioned three rollers driven member above-mentioned second at the interval of the above-mentioned first low lift cam and above-mentioned first roller follower, then above-mentioned first roller follower selects to use the needle roller roller, if the interval of the above-mentioned first low lift cam and above-mentioned first roller follower is over half the interval of the above-mentioned second low lift cam and above-mentioned three rollers driven member, then above-mentioned first roller follower selection use double-ring slip roller.
Therefore, with the littler three rollers driven member of lifting capacity as the slip roller structure, improve impact strength, even the three rollers driven member is kowtowed with big power and is hit the second low lift cam, also can transmit power by surface pressure, can not produce distortion or impression, make the abutment of the 3rd rocking arm become the structure that rigidity is taken in respect to the cam of the low lifting side of rotation, at least the second roller follower is with respect to high lift cam, as the needle roller roller, reduce friction, be the structure of having considered rotational resistance, and can have improved durability.
Description of drawings
Fig. 1 is the plan view of internal-combustion engine cap of the valve actuator of the expression example that has embodiments of the present invention one.
Fig. 2 is the enlarged view of the major component of Fig. 1.
Fig. 3 be among Fig. 2 the III-III line to view.
Fig. 4 be among Fig. 2 the IV-IV line to view.
Fig. 5 be among Fig. 2 the V-V line to view.
Fig. 6 is the sectional view of piston support part.
Fig. 7 is the oblique drawing from the rocking arm of camshaft flank observation.
Fig. 8 is the oblique drawing from the rocking arm of air inlet reveal observation.
Fig. 9 is the oblique drawing of the internal-combustion engine major component of expression pressurized oil system.
Figure 10 shows the sectional view of the installation situation of accumulator.
Figure 11 is the summary circuit diagram of pressurized oil system.
Symbol description
The 1st, cylinder head, 2, the 3rd, pitman arm shaft, the 4th, camshaft, 5 is first rocking arms, 6 is the 3rd rocking arms, and 7 is second rocking arms, the 8th, and piston-cylinder unit, 9 is first intake valves, 10 is first low lift cam, and 11 is second intake valves, and 12 is second low lift cam, the 13rd, and opening portion, the 14th, piston, the 15th, columnar portion, the 16th, grooving, the 17th, returning spring, the 18th, oil circuit, the 19th, path, the 20th, high lift cam, 21 is first roller followers, the 22nd, and interior roller, the 23rd, outer roller, 24 is three rollers driven member (slip rollers), 25, the 28th, needle bearing, 26, the 29th, outer roller, 27 is second roller follower (needle roller rollers), the 34th, and grooving face, the 35th, boss part, the 36th, pin, the 41st, oil pump, the 42nd, oily path, the 43rd, oil control valve, the 44th, pressure accumulation road, the 45th, accumulator, 46 is second filters, and 47 is first filters, the 48th, and the bypass path, the 51st, body, the 52nd, spring, the 53rd, piston, the 54th, spring seat, the 55th, stop ring, the 56th, outer screw section, the 61st, lid, the 62nd, deflection plate, the 63rd, dull and stereotyped.
Embodiment
Fig. 1 shows the plan view of cap of the internal-combustion engine that has valve actuator of the example of embodiments of the present invention one, Fig. 2 shows the amplification situation of the major component of Fig. 1, Fig. 3 be among Fig. 2 the III-III line to view, Fig. 4 be among Fig. 2 the IV-IV line to view, Fig. 5 be among Fig. 2 the V-V line to view, Fig. 6 shows the section of piston support part, Fig. 7 is the oblique drawing from the rocking arm of camshaft flank observation, Fig. 8 is the oblique drawing from the rocking arm of air inlet reveal observation, Fig. 9 is the oblique drawing of the internal-combustion engine major component of expression hydraulic system, Figure 10 shows the section of the installation situation of accumulator, and Figure 11 shows the summary loop situation of hydraulic system.
As shown in Figure 1, on cylinder head 1, be fixed with the pitman arm shaft 2 of air inlet side and the pitman arm shaft 3 of exhaust side abreast.On the cylinder head 1 between pitman arm shaft 2 and the pitman arm shaft 3, twelve Earthly Branches free to rotate are held camshaft 4.Illustrated internal-combustion engine adopts the structure that is respectively arranged with two intake valves and two exhaust valves on each cylinder of 4 cylinders in upright arrangement.
To shown in Figure 5, the twelve Earthly Branches that can freely swing respectively on pitman arm shaft 2 are held first Rocker arm 5 corresponding with each cylinder and the 3rd rocking arm 6 as Fig. 1, and on the pitman arm shaft 2 between first Rocker arm 5 and the 3rd rocking arm 6, the twelve Earthly Branches that can freely swing are held second rocking arm 7 of T word shape.On first Rocker arm 5 and the 3rd rocking arm 6, be formed with and be connected on the piston-cylinder unit 8 as the T word shape top 7a, the 7b that are connected piston-cylinder unit 8, the second rocking arms 7 of switching mechanism.
The top of first Rocker arm 5 is connected with first intake valve 9, and the cardinal extremity of first Rocker arm 5 is driven by the first low lift cam 10.The top of the 3rd rocking arm 6 is connected with second intake valve 11, and the cardinal extremity of the 3rd rocking arm 6 is driven by the second low lift cam 12 of lifting capacity less than the first low lift cam 10.In other words, first intake valve 9 regularly and with different lifting capacitys opens and closes with regulation respectively with second intake valve 11.In addition, the second low lift cam 12 also can select to allow in fact second intake valve 11 be in the intermittently shape of state.
As Fig. 3, Fig. 4, Fig. 7 and shown in Figure 8, be formed with piston-cylinder unit 8 respectively on first Rocker arm 5 and the 3rd rocking arm 6, T word shape top 7a, 7b with second rocking arm 7 on each piston-cylinder unit 8 are formed with opening portion 13a, 13b opposed to each other, on piston-cylinder unit 8, can have piston 14a, 14b with being free to slide, piston 14a, 14b have columnar portion 15a, the 15b with the inwall sliding contact of piston-cylinder unit 8, simultaneously, be formed with grooving 16a, the 16b that cuts opening portion 13a, 13b continuously on the top of columnar portion 15a, 15b.
Piston 14a, 14b are setovered downwards by returning spring 17a, 17b, make grooving 16a, 16b be in state (state of Fig. 4) in the face of opening portion 13a, 13b all the time.Axial portions at rocking arm 2 forms oil circuit 18, by oil pressure feed mechanism described later, with predetermined timing pressure oil is supplied with this oil circuit 18.Supply to the pressure oil in the oil circuit 18,,, can make piston 14a, 14b overcome the elastic force rising of returning spring 17a, 17b by with pressure oil supply cylinder unit 8 from path 19 supply cylinder unit 8.By the rising of the caused piston 14a of the supply of pressure oil, 14b, make columnar portion 15a, 15b be in state (state of Fig. 3) in the face of opening portion 13a, 13b.
To shown in Figure 5, T word shape top 7a, the 7b of second rocking arm 7 are connected with the inside of opening portion 13a, 13b as Fig. 1, and the cardinal extremity of second rocking arm 7 is driven by high lift cam 20.High lift cam 20 has the cam profile that comprises the first low lift cam 10 and the second low lift cam 12, and its lifting capacity is greater than the first low lift cam 10 and the second low lift cam 12.
Piston 14a, 14b by returning spring 17a, 17b towards below the application of force of setovering, grooving 16a, 16b are under the state (the not state of supply pressure oil) in the face of opening portion 13a, 13b, when driving second rocking arm 7 by high lift cam 20, grooving 16a, 16b in T word shape top 7a, the 7b of second rocking arm 7 and opening portion 13a, the 13b are opposed.Therefore, make under the situation of its swing by high lift cam 20 drivings second rocking arm 7, T word shape top 7a, the 7b of second rocking arm 7 embeds among (off state) grooving 16a, the 16b, and the swing of second rocking arm 7 is not delivered on first Rocker arm 5 and the 3rd rocking arm 6.
Therefore, by discharging the pressure oil of piston-cylinder unit 8,, first intake valve 9 is opened and closed respectively with predetermined timing and with different lifting capacitys with second intake valve 11 by means of the swing of first Rocker arm 5 and the 3rd rocking arm 6.
With pressure oil supply cylinder unit 8, the elastic force that makes piston 14a, 14b overcome returning spring 17a, 17b rises, and when making columnar portion 15a, 15b be in state in the face of opening portion 13a, 13b, columnar portion 15a, 15b in T word shape top 7a, the 7b of second rocking arm 7 and opening portion 13a, the 13b are opposed.Therefore, make under the situation of its swing by high lift cam 20 drivings second rocking arm 7, T word shape top 7a, 7b and columnar portion 15a, the 15b of second rocking arm 7 are abutted against (coupled condition), by piston-cylinder unit 8 swing of second rocking arm 7 are passed to first Rocker arm 5 and the 3rd rocking arm 6.
Thereby, by means of in the pressure oil supply cylinder unit 8, by the swing of caused first Rocker arm 5 of the swing of second rocking arm 7 and the 3rd rocking arm 6, first intake valve 9 and second intake valve 11 open and close with big lifting capacity simultaneously corresponding to the cam profile of high lift cam 20.
To the supply of piston-cylinder unit 8 and release, i.e. second rocking arm 7, first Rocker arm 5 and the coupled condition of the 3rd rocking arm 6 and the switching of off state of supply, is predefined according to vehicle running state (the rotational speed state of internal-combustion engine) with pressure oil.
For example, be under the situation of low speed in the rotational speed of internal-combustion engine, discharge to the pressure oil of piston-cylinder unit 8 and supply with, by the swing of first Rocker arm 5 and the 3rd rocking arm 6, regularly and with different lifting capacitys open and close first intake valve 9 and second intake valve 11 with regulation respectively.Thus, promote eddy current, strengening burning.And, rotational speed at internal-combustion engine is under the situation at a high speed, pressure oil is supplied with to piston-cylinder unit 8,, first intake valve 9 and second intake valve 11 are opened and closed simultaneously with big lifting capacity by means of the swing of caused first Rocker arm 5 of the swing of second rocking arm 7 and the 3rd rocking arm 6.Thus, guarantee a large amount of air inlets, strengthen output.
As Fig. 3 and shown in Figure 7, on 5 terminal sides and the abutment first low lift cam 10 of first rocking arm, be provided with first roller follower 21, make the cardinal extremity of first Rocker arm 5 be in first state that hangs down on the lift cam 10 that abuts against rotation with minimum drag by first roller follower 21.As shown in Figure 7, first roller follower 21 can constitute outer roller 26 by a plurality of needle bearings 25 with rotating freely, and outer roller 26 is contacted with first low lift cam 10 rollings.
As Fig. 4 and shown in Figure 7, on terminal side and the abutment second low lift cam 12 of the 3rd rocking arm 6, be provided with three rollers driven member 24, make the cardinal extremity of the 3rd rocking arm 6 be in second state that hangs down on the lift cam 12 that abuts against rotation with non-resistance by three rollers driven member 24.As shown in Figure 7, three rollers driven member 24 is formed with as the double-ring slip roller of interior roller 22 with outer roller 23.Interior roller 22 and outer roller 23 be state concentrically with respect to one another, is entrenched togather freely to rotate, and the outer roller 23 and the second low lift cam 12 are rolled and contacted.Double-ring slip roller is compared with the needle roller roller that uses needle bearing, and friction becomes big when roller rotates to be low speed rotation.Therefore, in order to reduce friction, implemented for example to make the polish fine finishing or the lubricated surface of usefulness of surface to handle (colloidal sol pasting processing) on the surface of interior roller 22.As a result, double-ring slip roller is compared with the needle roller roller, and friction is big when price height and roller low speed rotation.
As Fig. 5 and shown in Figure 7, on terminal side and the abutment high lift cam 20 of second rocking arm 7, be provided with second roller follower 27, by second roller follower 27 cardinal extremity of second rocking arm 7 be in non-resistance and abut against state on the high lift cam 20 of rotation.Second roller follower 27 can constitute outer roller 29 by a plurality of needle bearings 28 with rotating freely, and outer roller 29 is contacted with high lift cam 20 rollings.Therefore, during the high lift cam 20 of the high output of usage requirement, drive first intake valve 9 and second intake valves 11 by the needle roller roller 27 that rubs little, the loss of can reducing friction further improves and exports.
In addition, first roller follower 21 also can adopt the structure same with three rollers driven member 24, constitutes (double-ring slip roller) by interior roller 22 with outer roller 23, makes outer roller 23 and first hang down lift cam 10 rollings and contacts.
In addition, as shown in Figure 1, the twelve Earthly Branches that can freely swing on the pitman arm shaft 3 of exhaust side are held exhaust rocker arm 31a, 31b, and each exhaust rocker arm 31a, 31b drive by exhaust cam.
But, for example set for, the lifting capacity of high lift cam 20 caused first intake valves 9 and second intake valve 11 is big, how many lifting capacitys of producing less than high lift cam 20 of the lifting capacity of first low lift cam 10 caused first intake valves 9, and the lifting capacity of second low lift cam 12 caused second intake valves 11 is compared quite little with the lifting capacity that high lift cam 20 produces.
Therefore, to piston-cylinder unit 8 supply pressure oil (becoming coupled condition), and cause the swing of first Rocker arm 5 and the 3rd rocking arm 6 by means of the swing of second rocking arm 7, make under the situation that first intake valve 9 and second intake valve 11 open and close simultaneously with big lifting capacity the lifting capacity that the lifting capacity that high lift cam 20 produces is produced greater than the second low lift cam 12 and the first low lift cam 10.Thereby, can under the state of generation less than the gap at the interval of the second low lift cam 12 and three rollers driven member 24 between gap, the first low lift cam 10 and first roller follower 21 that generation is big between the second low lift cam 12 and the three rollers driven member 24, turn round.
Though its explanation has been omitted,, first Rocker arm 5, second rocking arm 7 and the 3rd rocking arm 6 are put to the cam lateral deviation all the time by biasing arrangement not shown in the figures.To piston-cylinder unit 8 supply pressures oil and cause the swing of first Rocker arm 5 and the 3rd rocking arm 6 by means of the swing of second rocking arm 7, make under the state of first intake valve 9 and 11 switchings of second intake valve, if discharge supply to the pressure oil of piston-cylinder unit 8, when promptly switching to the air inlet state, then discharge the transmission of the swing that second rocking arm 7 produced, make first Rocker arm 5 and the 3rd rocking arm 6 to the first low lift cam 10 and second low lift cam 12 side oscillations by biasing.
In this case, for example, if because when maximum lift, gap between the second low lift cam 12 and the three rollers driven member 24 becomes big, therefore, first Rocker arm 5 and the 3rd rocking arm 6 are biased power when the first low lift cam 10 and second low lift cam 12 side oscillations, and the three rollers driven member 24 and first roller follower 21 have and be in the possibility of kowtowing the state that hits the second low lift cam 12 and the first low lift cam 10.
Because the gap between first roller follower 21 and the first low lift cam 10 is very little, do not have big power effect, and the gap of the three rollers driven member 24 and the second low lift cam 12 is big, produces to kowtow to have big power effect when hitting.
Therefore, three rollers driven member 24 of the present invention has adopted the double-ring slip roller structure of interior roller 22 and outer roller 23.Because three rollers driven member 24 is a double-ring slip roller structure, therefore, can improve impact strength, even hit the second low lift cam 12 because of big power is kowtowed three rollers driven member 24, also can transmit power by surface pressure, can not produce distortion or impression, can eliminate the anxiety of damaging outer roller 23.
Thereby the abutment with respect to the second low lift cam 12 of rotating of the 3rd rocking arm 6 adopts the structure of having considered rigidity and rotational resistance.
In above-mentioned mode of execution example, in the internal-combustion engine that is provided with two kinds of little first different Rocker arm 5s of second rocking arm 7 lifting capacitys big and the 3rd rocking arm 6 with respect to lifting capacity, though example as double-ring slip roller, the big three rollers driven member 24 of lifting capacity difference has been described, but first roller follower 21 of the present invention also can adopt double-ring slip roller.
But, though double-ring slip roller has the advantage of high rigidity,, therefore the big shortcoming of friction when above-mentioned high price and rotor low speed rotation are also arranged, when first roller follower 21 adopts double-ring slip roller, must consider expense and service condition.For example, under the situation of the first low lift cam 10 for the shape that is similar to high lift cam 20, because the interval of the first low lift cam 10 and first roller follower 21 is little, so, preferably use the needle roller roller.On the contrary, under the situation of the first low lift cam 10 for the shape that is similar to the second low lift cam 12, because the interval of the first low lift cam 10 and first roller follower 21 is big, so, preferably use double-ring slip roller.In detail, if hang down below half of interval of lift cam 12 and three rollers driven member 24 second at the interval of the first low lift cam 10 and first roller follower 21, then select to use the needle roller roller, if the interval of the first low lift cam 10 and first roller follower 21 is over half the interval of the second low lift cam and three rollers driven member 24, then selection use double-ring slip roller.
In addition, spy as the claimant of this case application opens as shown in the 2001-41017, single intake valve type internal-combustion engine for the structure of switching two kinds of different rocking arms of lifting capacity, also can adopt the roller that is abutted against with cam as first roller follower, make the present invention of slip roller with the little side of lifting capacity.
In addition, as above-mentioned slip roller, though used double-ring slip roller,, also can adopt the monocycle shape slip roller that only forms by outer roller.But, under situation with monocycle shape slip roller, owing to compare poor durability with double-ring slip roller, and, the problem that further increase friction is arranged, so, the possibility that the output of the motor when having use first Lower speed cam 10 and second Lower speed cam 12 reduces, and, when using High speed cam 20, owing to make first intake valve 9 and 11 actions of second intake valve by the needle roller roller, so it is little to rub.Thereby, output bias between the output of the output of the motor when using High speed cam 20 and 10,12 o'clock motor of use Lower speed cam further increases, be easy to when switching High speed cam and Lower speed cam, produce the output change, have the possibility that causes runnability to worsen.Thereby the slip roller preferably uses double-ring slip roller.
As shown in Figure 8, because the top of piston 14 is formed with grooving 16, thereby returning spring 17 is configured in the position of staggering with the axle center of piston 14.Therefore, when piston 14 rotated around central shaft, the bias force of returning spring 17 was run counter to designing requirement.Therefore, in the present embodiment example,, be provided with the spline mechanism of piston 14 as Fig. 6, shown in Figure 7.
As Fig. 2, Fig. 6, shown in Figure 8, on the periphery at the position that is formed with grooving 16 of piston 14, be formed with grooving face 34, on the piston-cylinder unit 8 of first Rocker arm 5 and the 3rd rocking arm 6, be formed with boss 35 (with reference to Fig. 2) corresponding to grooving face 34.Grooving face 34 forms in the position of the opening portion 13 of avoiding piston-cylinder unit 8 and the back side of avoiding piston 14, will sell 36 on the grooving face 34 to contact and to be embedded in the state configuration on the grooving face 34 vertically.Pin 36 is fixed on the boss 35 by method such as being pressed into, pin 36 be adapted to make its central shaft with along extending on the parallel face of the horizontal plane of pitman arm shaft 2.
As spline mechanism, though also can on the horizontal plane of pitman arm shaft 2, set pin 36 towards right angle orientation etc.,, on right angle orientation etc., setting under the situation of pin 36, must on the columnar portion 15 of the bottom of piston 14, form the embedding part of pin 36.Because columnar portion 15 chimeric slip on piston-cylinder unit 8 is in the position that prevents oil leakage, therefore, when on columnar portion 15, forming the embedding part of pin 36, there is the possibility of oil leakage.So, with pin 36 be adapted to make its central shaft with along extending on the parallel face of the horizontal plane of pitman arm shaft 2.
When first Rocker arm 5 and the 3rd rocking arm 6 are swung by the swing of second rocking arm 7, be the back side of piston 14 from the position of bearing maximum load of second rocking arm, 7 sides.Therefore, pin 36 is provided in the oblique position at the back side of avoiding piston 14.In addition, pin 36 is fixed on the boss 35 of position of the opening portion 13 of avoiding piston-cylinder unit 8.Therefore, to piston 14 side shiftings, in addition, the transmission of the oscillatory forces by piston 14 also is to carry out on the whole back side from opening portion 13 for top 7a, the 7b that can not hinder second rocking arm 7.
Grooving face 34 forms at the intermediate portion of columnar portion 15, prevents that by means of pin 36 piston 14 from deviating to the outside.In addition, as Fig. 2, shown in Figure 8, the boss 35 of the piston-cylinder unit 8 on first Rocker arm 5 and the 3rd rocking arm 6 forms along same direction, and the grooving face 34 that is configured to piston 14 is towards same direction, and sells 36 states that are parallel to each other.Therefore, the piston 14 of first Rocker arm 5 and the 3rd rocking arm 6 can generalization, thereby can reduce the cost of component, prevents the generation of mistake assembling.
But, on the pitman arm shaft 2 of air inlet side, on each cylinder, supporting first Rocker arm 5, the 3rd rocking arm 6 and second rocking arm, 7, the first Rocker arm 5s and the 3rd rocking arm 6 to have switching mechanism, this switching mechanism has piston-cylinder unit 8 and piston 14.Therefore, compare with the valve switching mechanism of exhaust side, the valve switching mechanism of air inlet side is more complicated, and weight is big.
Thereby as shown in Figure 1, the diameter D1 of the pitman arm shaft 2 of air inlet side forms greater than the diameter D2 of the pitman arm shaft 3 of exhaust side (for example big 10% degree).Therefore, can guarantee the rigidity of the part that weight is big, improve the kinetic characteristic of valve actuation system.In addition,,, reduce the pressure loss of the pressure oil that flows by oil circuit 18, improve the performance of switching mechanism so also can increase the internal diameter of oil circuit 18 owing to increased the diameter D1 of pitman arm shaft 2.
Below, give row mechanism, be driving mechanism piston-cylinder unit 8 or piston 14 to the pressure oil of the oil circuit 18 of pitman arm shaft 2 based on Fig. 9 to Figure 11 explanation.
In the tip side of cylinder head 1, be formed with the oily path 42 that makes from the pressure oil circulation of oil pump 41 (with reference to Figure 11), oily path 42 is provided with the oil control valve 43 to row that is used to control to the pressure oil of oil circuit 18.Oily path 42 branches from the upstream side of oil control valve 43 are provided with pressure accumulation road 44, are connected with accumulator 45 on pressure accumulation road 44.Accumulator 45 is fixed on the cylinder head 1 as parts.
At the upstream side of oil control valve 43, on the oily path 42 of the upstream side of the branching portion on pressure accumulation road 44, be provided with second filter 46.Symbol 47 among Figure 11 is arranged on first filter of the discharge side of oil pump 41, and the 48th, make the bypass path of oil pump 41 bypass, on this bypass path, not shown relief valve is housed.
As shown in figure 10, accumulator 45 is provided with the tubular body 51 that vertically is fixed on the cylinder head 1, can have the piston 53 of being setovered by spring 52 downwards on tubular body 51 with being free to slide.The top of spring 52 is provided with spring seat 54 and stop ring 55, and spring 52 is in the state that is incorporated in the body 51.
Be formed with outer screw section 56 in the bottom of body 51,, accumulator 45 be fixed on the cylinder head 1 by outer screw section 56 is screwed in the female thread portion 57 of cylinder head 1.When being fixed on accumulator 45 on the cylinder head 1, the part on the top of body 51 is in state outstanding above cylinder head 1.By body 51 is fixed on the cylinder head 1, pressure accumulation road 44 is communicated with body 51, pressure oil is supplied to the downside of piston 53, the bias force that piston 53 overcomes spring 52 rises, and makes pressure oil pressure accumulation in body 51.
The top of cylinder head 1 is provided with covers 61, in order to collect smog, is provided with deflection plate 62 and dull and stereotyped 63 in lid 61.And, dull and stereotyped 63 be positioned at body outstanding above cylinder head 1 51 top directly over.Therefore, even dismounting stop choma 55 is deviate from, spring seat 54, spring 52, piston 53 also contact with dull and stereotyped 63 and prevent that it from outwards flying out.
The top of body 51 is set for shorter than the length S2 of outer screw section 56 with dull and stereotyped 63 interval S1, therefore, even body 51 is fixing lax with respect to the screw thread of cylinder head 1, body 51 is moved towards the direction (top) of deviating from, before being threaded of outer screw section 56 unclamped, the top of body 51 also can contact with dull and stereotyped 63, and body 51 can not deviate from.Therefore, can be not open towards the outside oily path 42 or pressure accumulation road 44.
Because the outer screw section 56 of body 51 usefulness the bottoms of accumulator 45 is fixed on the cylinder head 1, so, even produce oily sew etc., can not be leaked to the outside at fixing part yet.Thus, even be simplified to fix the sealing of portion, also can suppress leakage oil to the outside.In addition, body 51 fixing also can adopt and be pressed into combination fixing or by flange and retaining thread and the structure except that the mode of fixing by outer screw section 56 such as fix.
The pitman arm shaft 2 of above-mentioned formation in the row of the giving mechanism of the pressure oil of oil circuit 18, when by the driving of oil pump 41 from oily path 42 during to pressure accumulation road 44 supply pressures oil, pressure oil is filtered by second filter 46, and supplies to the pitman arm shaft 3 of oil control valve 43 and accumulator 45, exhaust side.Be at oil control valve 43 under the situation of OFF (closing) state,, pressure oil saved in the accumulator 45 by means of the oil pressure on pressure accumulation road 44.
When motor rotated with the speed of regulation, owing to switch by the driving of high lift cam 20, therefore, oil control valve 43 was in ON (opening) state.Pressure oil flows in the oil circuit 18 of the pitman arm shaft 2 of air inlet side sharp via oil control valve 43.At this moment, the delivery volume deficiency of pressure oil, the oil pressure on oily path 42 and pressure accumulation road 44 temporarily can reduce, so the pressure oil of savings is released the deficiency of supplementary pressure oil by the elastic force of spring 52 in the accumulator 45.
Therefore, even for a cylinder switching mechanism of two piston-cylinder units 8 is arranged, the deficiency of pressure oil can not appear also, and can be with better response supply pressure oil.
Owing to be provided with second filter 46, therefore can remove the foreign matter that is included in the pressure oil that accumulator 45 saved at the upstream side of accumulator 45.Therefore, foreign matter can not immerse in the body 51 of accumulator 45, can not produce stick-slip on the piston 53.
The pressure oil of releasing from accumulator 45 can not pass through second filter 46, but flow to oil control valve 43, therefore, the influence of the pressure loss that produces because of flowing can be eliminated, the oil circuit 18 of pitman arm shaft 2 can be pressure oil supplied to good responsiveness through second filter 46.
As the internal-combustion engine of the structure that adopts above-mentioned accumulator 45 and the internal-combustion engine that employing is provided with the loop structure of second filter 46, with the structure that has the switching mechanism that is made of first Rocker arm 5, the 3rd rocking arm 6 and second rocking arm 7 is that example is illustrated, but, also applicable to the internal-combustion engine of the switching mechanism that has other structures.For example, as the spy of the claimant of this case application open disclose among the 2001-41017, for single intake valve type internal-combustion engine of the structure of switching two kinds of different rocking arms of lifting capacity, also can adopt the structure of accumulator 45, or adopt the loop structure that is provided with second filter 46.
In addition, in above-mentioned mode of execution example, enumerate cam changeover mechanism is arranged on example on the pitman arm shaft 2 of air inlet side, be illustrated, still, will carry out the situation that mechanism that cam switches is arranged on exhaust side and also be suitable for.
The invention effect
In order to achieve the above object, the valve actuator of internal combustion engine of the present invention comprises: rocker arm shaft; The top is connected with first inlet valve or first row valve, can be supported in above-mentioned rocker arm shaft with freely swinging On, by first rocking arm of the first low lift cam driving; Top and second inlet valve or second exhaust Door connects, and can be supported on the above-mentioned rocker arm shaft with freely swinging, is hanged down less than first by lifting capacity to promote The 3rd rocking arm that the second low lift cam of cam drives; Be provided with and connect with the above-mentioned first rocking arm side The top that connects can be supported on the above-mentioned rocker arm shaft with freely swinging, by lifting capacity greater than above-mentioned first Second rocking arm that the high lift cam of low lift cam drives; Be arranged on the cardinal extremity of above-mentioned first rocking arm Side is hanged down first roller follower that lift cam is abutted against with above-mentioned first of camshaft; Be arranged on State the base end side of the 3rd rocking arm, hang down the three rollers that lift cam is abutted against with second of above-mentioned camshaft Driven member; Be arranged on the base end side of above-mentioned second rocking arm, protruding with the above-mentioned high lifting of above-mentioned camshaft Second roller follower that wheel is abutted against; Reach for switching above-mentioned second rocking arm and shake with respect to above-mentioned first The switching mechanism that is connected of the connection status of arm and the 3rd rocking arm and off-state, above-mentioned first roller from At least above-mentioned second roller follower in moving part and above-mentioned second roller follower is as using needle roller The needle roller roller of bearing forms, and is supported in the base end side of above-mentioned first rocking arm, above-mentioned three rollers Driven member forms as double-ring slip roller, and is supported in the base end side of above-mentioned the 3rd rocking arm, as The interval of the fruit above-mentioned first low lift cam and above-mentioned first roller follower is above-mentioned second low the lifting Below half of the interval of cam and above-mentioned three rollers driven member, above-mentioned first roller follower then Choice for use needle roller roller, if the above-mentioned first low lift cam and above-mentioned first roller follower The interval is over half the interval of the above-mentioned second low lift cam and above-mentioned three rollers driven member, The above-mentioned first roller follower choice for use double-ring slip roller then
Therefore, as the slip roller structure, improve punching with the littler three rollers driven member of lifting capacity Hit intensity is even the three rollers driven member also can pass through with the big power knocking second low lift cam Surface pressing transmits power, can not produce distortion or impression, makes the low with respect to what rotate of the 3rd rocking arm The abutment that promotes the cam of side becomes the structure that rigidity is taken in, and promotes with respect to height at least Second roller follower of cam is reduced friction as the needle roller roller, and rotational resistance is examined The structure of considering, and improved durability.
Claims (1)
1. the valve actuator of internal-combustion engine comprises:
Pitman arm shaft;
The top is connected with first intake valve or first exhaust valve, can be supported on the above-mentioned pitman arm shaft, by first rocking arm of the first low lift cam driving with freely swinging;
The top is connected with second intake valve or second exhaust valve, can be supported on the above-mentioned pitman arm shaft, by three rocking arm of lifting capacity less than the second low lift cam driving of the first low lift cam with freely swinging;
Be provided with the top that can be connected, can be supported on the above-mentioned pitman arm shaft with freely swinging, by second rocking arm of lifting capacity greater than the high lift cam driving of the above-mentioned first low lift cam with the above-mentioned first rocking arm side;
Be arranged on the terminal side of above-mentioned first rocking arm, hang down first roller follower that lift cam is abutted against with above-mentioned first of camshaft;
Be arranged on the terminal side of above-mentioned the 3rd rocking arm, hang down the three rollers driven member that lift cam is abutted against with second of above-mentioned camshaft;
Be arranged on the terminal side of above-mentioned second rocking arm, second roller follower that is abutted against with the above-mentioned high lift cam of above-mentioned camshaft; And
Be used to switch the be connected switching mechanism of above-mentioned second rocking arm with respect to coupled condition with the off state of above-mentioned first rocking arm and the 3rd rocking arm,
It is characterized in that,
Above-mentioned at least second roller follower in above-mentioned first roller follower and above-mentioned second roller follower forms as the needle roller roller that uses needle bearing, above-mentioned three rollers driven member forms as double-ring slip roller, if hang down below half of interval of lift cam and above-mentioned three rollers driven member above-mentioned second at the interval of the above-mentioned first low lift cam and above-mentioned first roller follower, then above-mentioned first roller follower selects to use the needle roller roller, if the interval of the above-mentioned first low lift cam and above-mentioned first roller follower is over half the interval of the above-mentioned second low lift cam and above-mentioned three rollers driven member, then above-mentioned first roller follower selection use double-ring slip roller.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP364599/2002 | 2002-12-17 | ||
| JP2002364599 | 2002-12-17 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1514114A CN1514114A (en) | 2004-07-21 |
| CN100393987C true CN100393987C (en) | 2008-06-11 |
Family
ID=34260215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101214387A Expired - Fee Related CN100393987C (en) | 2002-12-17 | 2003-12-16 | Air valve driver for IC engine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN100393987C (en) |
| TW (1) | TWI222489B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8627791B2 (en) * | 2011-05-26 | 2014-01-14 | Jacobs Vehicle Systems, Inc. | Primary and auxiliary rocker arm assembly for engine valve actuation |
| JP6090230B2 (en) * | 2014-05-14 | 2017-03-08 | トヨタ自動車株式会社 | Control device for internal combustion engine and variable valve operating device for internal combustion engine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4727831A (en) * | 1985-07-31 | 1988-03-01 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating mechanism for internal combustion engine |
| JPH0893418A (en) * | 1994-09-20 | 1996-04-09 | Sumitomo Electric Ind Ltd | Roller locker arm |
| US5553584A (en) * | 1993-12-24 | 1996-09-10 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating device for internal combustion engine |
| JP2001041017A (en) * | 1999-07-30 | 2001-02-13 | Mitsubishi Motors Corp | Variable valve mechanism |
| CN1301912A (en) * | 1999-12-28 | 2001-07-04 | 本田技研工业株式会社 | Valve operation system in IC engine |
-
2003
- 2003-11-12 TW TW92131633A patent/TWI222489B/en not_active IP Right Cessation
- 2003-12-16 CN CNB2003101214387A patent/CN100393987C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4727831A (en) * | 1985-07-31 | 1988-03-01 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating mechanism for internal combustion engine |
| US5553584A (en) * | 1993-12-24 | 1996-09-10 | Honda Giken Kogyo Kabushiki Kaisha | Valve operating device for internal combustion engine |
| JPH0893418A (en) * | 1994-09-20 | 1996-04-09 | Sumitomo Electric Ind Ltd | Roller locker arm |
| JP2001041017A (en) * | 1999-07-30 | 2001-02-13 | Mitsubishi Motors Corp | Variable valve mechanism |
| CN1301912A (en) * | 1999-12-28 | 2001-07-04 | 本田技研工业株式会社 | Valve operation system in IC engine |
Also Published As
| Publication number | Publication date |
|---|---|
| TWI222489B (en) | 2004-10-21 |
| CN1514114A (en) | 2004-07-21 |
| TW200413632A (en) | 2004-08-01 |
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Granted publication date: 20080611 Termination date: 20201216 |