CN203335158U - Fixedly-hinged type engine variable valve driving mechanism - Google Patents
Fixedly-hinged type engine variable valve driving mechanism Download PDFInfo
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- CN203335158U CN203335158U CN2013202557519U CN201320255751U CN203335158U CN 203335158 U CN203335158 U CN 203335158U CN 2013202557519 U CN2013202557519 U CN 2013202557519U CN 201320255751 U CN201320255751 U CN 201320255751U CN 203335158 U CN203335158 U CN 203335158U
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Abstract
A fixedly-hinged type engine variable valve driving mechanism comprises a box body, a driving mechanism body and a carrying mechanism. The driving mechanism body comprises a driving piston and driving springs, and the driving piston is placed in a driving piston hole of the box body and is provided with a non-operating position and an operating position. In general, oil pressure inside the box body enables the driving piston to be maintained at the non-operating position, and the carrying mechanism is separated from an air valve of an engine. When the oil pressure is lowered or removed, the driving springs enable the driving piston to be moved to the operating position from the non-operating position, the carrying mechanism of a variable valve driving system is in solid hinged connection with the air valve of the engine, loads or movement is transmitted to the air valve of the engine in a mechanical mode, and therefore the air valve movement of the engine is generated. By means of the fixedly-hinged type engine variable valve driving mechanism, the defects of deformation, leakage, unstable operation, unreliable running and the like caused by hydraulic type driving and carrying are overcome, the main valve movement function of the engine is added, and braking, discharging and starting of the engine are improved.
Description
Technical field:
The utility model relates to mechanical field, relates in particular to the valve actuation technology of vehicle motor, particularly a kind of engine variable-valve driving mechanism of solid chain type.
Background technique:
In prior art, the throttle actuation technology of vehicle motor is behaved and is known altogether, its application history of existing more than 100 year.But due to other demands such as motor discharge, braking and cold start-ups, increasing motor need to be on the basis of throttle motion, increase auxiliary valve motion, in the on-board engine applicating history of more than 100 years, the throttle actuator adopts is all that the connection of solid chain type (non-hydraulic type) drives and carries, the camming movement of motor is mechanically passed to valve, produce the throttle motion.And current applied motor auxiliary valve drive unit in the world is mostly to adopt the connection of hydraulic type drive and carry, produce auxiliary valve motion.The driving of hydraulic type and carrying have the shortcomings such as distortion, leakage, fluctuation of service and operation be unreliable.In addition, traditional motor throttle drive system makes the cold start-up of motor very difficult, and the driving of hydraulic type and carrying also are difficult to improve the cold start-up of motor.
Summary of the invention:
The purpose of this utility model is to provide a kind of engine variable-valve driving mechanism of solid chain type.The engine variable-valve driving mechanism of described this solid chain type to solve that hydraulic type in prior art drives and the motor auxiliary valve drive unit of carrying in hydraulic pressure distortion, leakage, fluctuation of service and the insecure technical problem of operation, and the technical problem of engine cold-start difficulty.
The engine variable-valve driving mechanism of this solid chain type of the present utility model, comprise casing, driving mechanism and load bearing mechanism, described casing contains driven plunger hole and fluid passage, described driving mechanism comprises driven plunger and driving spring, described driven plunger is placed in the driven plunger hole in casing, described driving spring is placed in an end of driven plunger, the other end of driven plunger is near described fluid passage, it is characterized in that: described driven plunger has off position and operating position in the driven plunger hole in described casing, the driving spring of driven plunger one end is shifted to operating position by driven plunger from off position, the active force that fluid in the fluid passage of the driven plunger the other end produces is shifted to off position by driven plunger from operating position, operating position in driven plunger, described load bearing mechanism links with the valve formation solid of motor, by load or movable machinery formula be delivered to the valve of motor, produce the valve motion of motor, off position in driven plunger, the valve of described load bearing mechanism and motor is separated, interaction between the valve of elimination and motor.
Further, the engine variable-valve driving mechanism of described solid chain type driving mechanism also comprise resetting piston, described resetting piston and driven plunger are basically on same axis, and an end of resetting piston is near driven plunger, and the other end of resetting piston is to fluid passage.
Further, driven plunger or the resetting piston of the driving mechanism of the engine variable-valve driving mechanism of described solid chain type contain guiding groove, described load bearing mechanism comprises connecting rod and loading piston, described connecting rod is positioned at guiding groove, described driven plunger becomes vertical position by the connecting rod in guiding groove from oblique position, the upper end of connecting rod passes to casing by load, and the lower end of connecting rod passes to loading piston by load.
Further, the load bearing mechanism of the engine variable-valve driving mechanism of described solid chain type comprises depression bar or the valve bridge itself be placed in the engine valve bridge.
Further, the engine valve movement of the engine variable-valve driving mechanism of described solid chain type comprises following auxiliary valve motion:
1) for the valve motion of engine braking, the valve motion of described engine braking comprises lose heart type braking valve motion and compression-release braking valve motion,
2) for the valve motion of engines exhaust gas recirculation, and
3) for the valve motion of engine start.
Further, the casing of the engine variable-valve driving mechanism of described solid chain type has different kinds, comprising:
1) be placed on motor and static casing relative to motor, or,
2) piston of relative movement is arranged with motor, or,
3) rocking arm of motor, or,
4) the valve bridge of motor.
Working principle of the present utility model is: when needing the auxiliary valve motion of motor, reduce and eliminate the hydrodynamic pressure (oil pressure) in the engine variable-valve drive system even fully, utilize driving spring mechanically driven plunger to be moved on to operating position from off position, Variabale valve actuation system links with the valve formation solid of motor, its load bearing mechanism by load or movable machinery formula be delivered to the valve of motor, produce the auxiliary valve motion of motor.When not needing the auxiliary valve motion of motor, improve the hydrodynamic pressure in Variabale valve actuation system, overcome the active force of driving spring, driven plunger is moved back into to off position from operating position, Variabale valve actuation system separates with the valve of motor, eliminate the interaction between the valve of load bearing mechanism and motor, lose the auxiliary valve motion of motor.
The utility model is compared with prior art, and its effect is actively with obvious.The engine variable-valve driving mechanism of solid chain type of the present utility model adopts mechanical type to drive and solid chain type carrying produces the auxiliary valve motion of motor, has eliminated the shortcomings such as the driving of hydraulic type and distortion, leakage, fluctuation of service and operation that carrying brings be unreliable.In addition, the auxiliary valve motion that mechanical type of the present utility model drives and carrying produces can increase the function of throttle motion, produces engine braking, the discharge that improves motor and cold start-up.
The accompanying drawing explanation:
Fig. 1 is the schematic diagram of first embodiment in non-operating state of the engine variable-valve driving mechanism of solid chain type of the present utility model.
Fig. 2 is the schematic diagram of first embodiment in serviceability of the engine variable-valve driving mechanism of solid chain type of the present utility model.
Fig. 3 is the interior schematic diagram of rocking arm that first embodiment of the engine variable-valve driving mechanism of solid chain type of the present utility model is integrated in motor.
Fig. 4 is the schematic diagram of second embodiment in non-operating state of the engine variable-valve driving mechanism of solid chain type of the present utility model.
Fig. 5 is a kind of application schematic diagram of second embodiment of the engine variable-valve driving mechanism of chain type admittedly of the present utility model.
Embodiment:
Embodiment 1:
Fig. 1, Fig. 2 and Fig. 3 are for describing embodiment one.
What Fig. 1 and Fig. 2 described is that first embodiment of the present utility model is respectively in non-operating state and serviceability, Gu the engine variable-valve driving mechanism 100 of chain type comprises casing 210, driving mechanism and load bearing mechanism.Casing 210 contains 166He fluid passage, driven plunger hole 214.Driving mechanism comprises driven plunger 164 and driving spring 156.Driven plunger 164 is placed in the driven plunger hole 166 in casing 210, driving spring 156 is placed in an end (left end in figure) of driven plunger 164, the other end of driven plunger 164 (right-hand member in figure) is near fluid passage 214, and guiding groove 270 is contained at the middle part of driven plunger 164.Load bearing mechanism comprises connecting rod 184 and loading piston 160, loading piston 160 is positioned at the loading piston hole 190 of casing 210, connecting rod 184 is positioned at guiding groove 270, the upper end 122 of connecting rod 184 forms spherical revolute pair with the bottom surface of guiding groove 270, by driven plunger 164, load is upwards passed to casing 210; The lower end 128 of connecting rod 184 and form another spherical rotation pair above loading piston between 126, by the load going down to loading piston 160.The lower end of loading piston 160 by a preloading spring 177 by loading piston 160 biasings upwards.Preloading spring 177 is fixed tightly on casing 210 by screw 179.
There is off position (Fig. 1) and operating position (Fig. 2) in the driven plunger hole 166 of driven plunger 164 in described casing 210, driving spring 156 moves on to operating position by driven plunger 164 from off position, and the active force that the fluids in fluid passage 214 produce on driven plunger 164 enough large in, can overcome the active force of driving spring 156, driven plunger 164 is moved back into to off position from operating position.At the operating position (Fig. 2) of driven plunger 164, connecting rod 184 becomes vertical position (Fig. 2) from oblique position (Fig. 1), causes loading piston 160 to become outward extended position (Fig. 2) from retracted position (Fig. 1) in loading piston hole 190.
It is below the working procedure of the present embodiment.The engine variable-valve driving mechanism 100 of solid chain type of the present utility model is normally in the non-operating state shown in Fig. 1, hydrodynamic pressure (oil pressure) in fluid passage 214 overcomes the active force of driving spring 156, driven plunger 164 is pressed against to the left side (spring seat) 158 top (there is a drain tap 168 centre) of piston hole 166 left, in off position.Connecting rod 184 becomes oblique position, under the effect of loading piston 160 preloading spring 177 in its lower section below connecting rod, upwards retracts, and has eliminated contact or the link of the valve of motor.When needs are opened Variabale valve actuation system 100, while producing the auxiliary valve motion of motor, can pass through a kind of liquid control system (not showing) here, reduce the interior hydrodynamic pressure (oil pressure) of eliminate fluid passage 214 even fully, driving spring 156 presses against driven plunger 164 right side 246 of piston hole 166 to the right, in operating position (Fig. 2).Connecting rod 184 becomes vertical position from oblique position, and the loading piston 160 below connecting rod stretches out downwards piston hole 190 is interior, forms solid with following engine valve (Fig. 3) and links.
Fig. 3 is the interior schematic diagram of rocking arm that first embodiment of the present utility model is integrated in motor.Valve actuator 200 shown in figure comprises cam 230, tappet roller 235, push rod 201, rocking arm 210, conventional valve clearance regulating system, Variabale valve actuation system 100 and valve bridge 400.Conventional valve clearance regulating system comprises adjusting screw 110 and tightens up nut 105.Another one valve clearance regulating system is in push rod one side, can regulate the gap 132 between Variabale valve actuation system 100 and valve, comprise adjusting screw 110b and tighten up nut 105b, two valves 300 (300a and 300b) of motor be positioned at valve bridge 400 both sides below, valve spring 310 (310a and 310b) by motor is biased on the valve seat 320 of engine cylinder-body 500, stops gas to flow between engine cylinder and outlet pipe 600.Rocking arm 210 is arranged on pitman arm shaft 205 rock typely.One end of rocking arm 210 is connected with cam 230 with roller 235 by push rod 201, and cam 230 has conventional boss 220 and auxiliary boss 232 and 233 of having strengthened on interior basic circle 225.The position of Fig. 3 cam 230 in basic circle 225, anti-fly off spring 198 by rocking arm 210 counter-clockwise be biased on cam, in rocking arm 210(adjusting screw 110) and valve bridge 400 between and Variabale valve actuation system 100(loading piston 160) and valve 300a(depression bar 116) between form respectively valve clearance 130 and 132.
Variabale valve actuation system 100 shown in Fig. 3 is in non-operating state.Liquid control system (not showing here), such as an open type two-position three way magnetic valve (when open type refers to that coil is not switched on, stream is opened), fluid (as machine oil), from otch 213 and fluid passage 214 in the axial bore 211 in pitman arm shaft 205 and radial hole 212, rocking arm, is supplied with to driven plunger 164.Oil pressure overcomes the active force of driving spring 156, shift driven plunger 164 onto off position left, 184 one-tenth heeling conditions of connecting rod, upwards retract under the effect of loading piston 160 preloading spring 177 in its lower section below connecting rod, and form gap 132 between depression bar 116.Auxiliary boss 232 above cam 230 and 233 motion are because gap 130 and 132 and can not pass to the valve 300 of motor, only have the motion that strengthens boss 220 upper parts can pass through rocking arm 210 and valve bridge 400, pass to valve 300, produce the throttle motion (conventional valve motion) of motor.
When needs are opened Variabale valve actuation system 100, while producing the auxiliary valve motion of motor, the coil electricity of open type two-position three way magnetic valve recited above, close closed channel and unload stream, oil pressure in fluid passage 214 reduces even fully to be eliminated, and driving spring 156 is pushed driven plunger 164 to operating position to the right, and connecting rod 184 becomes vertical state, loading piston 160 below connecting rod stretches out downwards piston hole 190 is interior, eliminate and depression bar 116 between gap 132.Now, Variabale valve actuation system 100 forms solid with valve 300a and links, and is delivered to the auxiliary boss 232 above cam 230 and 233 movable machinery formula the valve 300a of motor, produces the auxiliary valve motion of motor.
Embodiment 2:
Fig. 4 and Fig. 5 are for describing embodiment two.
Fig. 4 is the schematic diagram of second embodiment of the present utility model in non-operating state.With first embodiment in Fig. 1, compare, the present embodiment has increased connecting rod (lower link) 186 and resetting piston 162.Resetting piston 162 is placed in the resetting piston hole 260 of casing 210b, with driven plunger 164 basically on same axis.One end of resetting piston 162 (right-hand member in Fig. 4) is near driven plunger 164, and the other end of resetting piston 162 (left end in Fig. 4) is towards fluid passage 214.The load bearing mechanism of Variabale valve actuation system 100 comprises connecting rod 184 and 186 and loading piston 160.Connecting rod (upper connecting rod 184 and lower link 186) is positioned at the guiding groove 137 of resetting piston 162, the upper end 122 of upper connecting rod 184 passes to casing 210b by valve clearance adjusting screw 110b by load, the upper end of the lower end of upper connecting rod 184 and lower link 186 forms an auxiliary connection at 125 places, and the lower end 128 of lower link 186 passes to loading piston 160 by load.In Fig. 4 in fluid passage 214 active force of fluid on resetting piston 162 left sides overcome the active force of driving spring 156 on driven plunger 164 right sides, driven plunger 164 is in off position, connecting rod 184 and 186 is in oblique position, loading piston 160 in loading piston hole 190 in retracted position.
Fig. 5 is second embodiment's an application schematic diagram.The throttle actuator 200 of motor comprises cam 230, tappet roller 235, rocking arm 210 and valve bridge 400.Valve clearance regulating system in practical application does not show here.Rocking arm 210 is arranged on pitman arm shaft 205 rock typely.One end of rocking arm 210 is connected with cam 230 by roller 235, and cam 230 has a conventional boss 220 on interior basic circle 225, for the conventional valve motion (or throttle motion) of motor.
Variabale valve actuation system 100 in non-operating state in Fig. 5 is positioned at the top of a valve 300a of motor, loading piston 160 and be placed between the briquetting 116 in valve bridge 400 gap 132 is arranged, Variabale valve actuation system 100 is separated with the valve of motor, the interaction between the valve of elimination loading piston 160 and motor.
When needs are opened Variabale valve actuation system 100, while producing the auxiliary valve motion of motor, can be by the coil electricity of open type two-position three way magnetic valve recited above, close closed channel and unload stream, oil pressure in fluid passage 214 is reduced even fully and eliminates, and driving spring 156 is pushed driven plunger 164 to operating position, and connecting rod becomes vertical position from inclination, loading piston 160 below connecting rod stretches out downwards, the gap 132 between elimination and depression bar 116.Now, Variabale valve actuation system 100 forms solid with valve 300a and links, by load or movable machinery formula be delivered to the valve 300a of motor, produce the auxiliary valve motion of motor, comprising the valve motion for air-leakage type engine braking, compression-release engine braking, engines exhaust gas recirculation and engine start.
For instance, when the casing 210b of Variabale valve actuation system 100 is fixed on motor (motor is static relatively), the stroke of loading piston 160 can be arranged to such an extent that be greater than gap 132.Like this, the Variabale valve actuation system 100 in serviceability will make the valve 300a of motor keep the constant perseverance to open, and produce the auxiliary valve motion for the cold start-up of the engine braking of the type that loses heart or motor.In addition, when the casing 210b of Variabale valve actuation system 100 is an auxiliary rocker arm, the motion of auxiliary cam can be by the load bearing mechanism of Variabale valve actuation system in auxiliary rocker arm and auxiliary rocker arm, mechanically be delivered to the valve 300a of motor, produce the auxiliary valve motion of the cold start-up of the EGR of engine braking for compression-release, motor or motor.
Above-mentioned explanation has comprised a lot of concrete mode of executions, and this should not be regarded as the restriction to the utility model scope, but, as representing concrete illustrations more of the present utility model, many other develop all and likely therefrom produce.For instance, the engine variable-valve driving mechanism of the solid chain type shown here, not only can be used for overhead cam engine, also can be used for push rod/pushing type motor; Not only can be used for driving exhaust valve, also can be used to drive into valve; Not only can be for a valve, also can be for plural valve.
In addition, the engine variable-valve driving mechanism of the solid chain type shown here, can be not only piston crank mechanism, can be also other solid chain mechanism, as slide mechanism, rotating mechanism, profile of tooth mechanism, step piston mechanism, oblique mechanism, eccentric stiffener and lock ball mechanism etc.
Also have, the reduction shown is here even eliminated and improved the mode of hydrodynamic pressure in the engine variable-valve drive system can be different.Fluid wherein can be liquid, as the lubricating oil of motor self, can be also gas; Here the liquid control system of mentioning, except normal-open electromagnetic valve, can be also other control mechanism.
In addition, the casing shown here can have different kinds, comprising: be placed on motor and static casing relative to motor, with motor, the valve bridge etc. of the piston of relative movement, engine-mounted rocking arm and motor arranged.
Also have, the load bearing mechanism of the engine variable-valve driving mechanism of the solid chain type shown here, except comprising connecting rod, loading piston and briquetting, can also be the existing component of motor self such as the component of other form, or even valve bridge or rocking arm.
Therefore, scope of the present utility model should not decided by above-mentioned concrete illustration, but is decided by affiliated claim and the suitable right of law thereof.
Claims (6)
1. the engine variable-valve driving mechanism of a solid chain type, comprise casing, driving mechanism and load bearing mechanism, described casing contains driven plunger hole and fluid passage, described driving mechanism comprises driven plunger and driving spring, described driven plunger is placed in the driven plunger hole in casing, described driving spring is placed in an end of driven plunger, the other end of driven plunger is near described fluid passage, it is characterized in that: described driven plunger has off position and operating position in the driven plunger hole in described casing, the driving spring of driven plunger one end is setovered from off position driven plunger to operating position, fluid force in the fluid passage of the driven plunger the other end is setovered from operating position driven plunger to off position, operating position in driven plunger, described load bearing mechanism links with the valve formation solid of motor, by load or movable machinery formula be delivered to the valve of motor, produce the valve motion of motor, off position in driven plunger, the valve of described load bearing mechanism and motor is separated, interaction between the valve of elimination and motor.
2. the engine variable-valve driving mechanism of solid chain type as claimed in claim 1, it is characterized in that: described driving mechanism also comprises resetting piston, described resetting piston and driven plunger are basically on same axis, one end of resetting piston is near driven plunger, and the other end of resetting piston is to fluid passage.
3. the engine variable-valve driving mechanism of solid chain type as claimed in claim 1 or 2, it is characterized in that: driven plunger or the resetting piston of described driving mechanism contain guiding groove, described load bearing mechanism comprises connecting rod and loading piston, described connecting rod is positioned at guiding groove, described driven plunger becomes vertical position by the connecting rod in guiding groove from oblique position, the upper end of connecting rod passes to casing by load, and the lower end of connecting rod passes to loading piston by load.
4. the engine variable-valve driving mechanism of solid chain type as claimed in claim 1, it is characterized in that: described load bearing mechanism comprises depression bar or the valve bridge itself be placed in the engine valve bridge.
5. the engine variable-valve driving mechanism of solid chain type as claimed in claim 1, it is characterized in that: described engine valve movement comprises following auxiliary valve motion:
1) for the valve motion of engine braking, the valve motion of described engine braking comprises lose heart type braking valve motion and compression-release braking valve motion,
2) for the valve motion of engines exhaust gas recirculation, and
3) for the valve motion of engine start.
6. the engine variable-valve driving mechanism of solid chain type as claimed in claim 1, it is characterized in that: described casing comprises:
1) be placed on motor and static casing relative to motor, or,
2) piston of relative movement is arranged with motor, or,
3) rocking arm of motor, or,
4) the valve bridge of motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202557519U CN203335158U (en) | 2013-05-13 | 2013-05-13 | Fixedly-hinged type engine variable valve driving mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202557519U CN203335158U (en) | 2013-05-13 | 2013-05-13 | Fixedly-hinged type engine variable valve driving mechanism |
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| Publication Number | Publication Date |
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| CN203335158U true CN203335158U (en) | 2013-12-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013202557519U Expired - Fee Related CN203335158U (en) | 2013-05-13 | 2013-05-13 | Fixedly-hinged type engine variable valve driving mechanism |
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| CN (1) | CN203335158U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104712396A (en) * | 2015-03-04 | 2015-06-17 | 上海尤顺汽车部件有限公司 | Engine braking device |
| CN107035450A (en) * | 2015-10-16 | 2017-08-11 | 现代自动车株式会社 | Changeable air valve opens duration/variable valve lift system and engine |
| CN107956530A (en) * | 2016-10-18 | 2018-04-24 | 上海尤顺汽车部件有限公司 | A kind of slow seating arrangement for slowing down valve crash speed |
| CN110486113A (en) * | 2019-08-19 | 2019-11-22 | 上海尤顺汽车部件有限公司 | A kind of engine valve actuations mechanism |
-
2013
- 2013-05-13 CN CN2013202557519U patent/CN203335158U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104712396A (en) * | 2015-03-04 | 2015-06-17 | 上海尤顺汽车部件有限公司 | Engine braking device |
| CN107035450A (en) * | 2015-10-16 | 2017-08-11 | 现代自动车株式会社 | Changeable air valve opens duration/variable valve lift system and engine |
| CN107035450B (en) * | 2015-10-16 | 2020-12-11 | 现代自动车株式会社 | Variable valve opening duration and variable valve lift system and engine |
| CN107956530A (en) * | 2016-10-18 | 2018-04-24 | 上海尤顺汽车部件有限公司 | A kind of slow seating arrangement for slowing down valve crash speed |
| CN110486113A (en) * | 2019-08-19 | 2019-11-22 | 上海尤顺汽车部件有限公司 | A kind of engine valve actuations mechanism |
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| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131211 Termination date: 20210513 |