CN1139178A - Eccentric-wheel (cam) hydraulic air gate mechanism - Google Patents
Eccentric-wheel (cam) hydraulic air gate mechanism Download PDFInfo
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- CN1139178A CN1139178A CN95107511A CN95107511A CN1139178A CN 1139178 A CN1139178 A CN 1139178A CN 95107511 A CN95107511 A CN 95107511A CN 95107511 A CN95107511 A CN 95107511A CN 1139178 A CN1139178 A CN 1139178A
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- cam
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- eccentric wheel
- plunger
- oil
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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
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
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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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
In the gas distributing mechanism for four-stroke engine, there are an eccentric wheel or cam coaxial with large othorchronous wheel and a hydraulic mechanism including main cylinder with plunger and othorchronous relief hole, axiliary cylinder with overflow hole, compensation oil path and othorchronous regulating plate, which is coaxial with and able to rotate by certain angle to the eccentric wheel or cam and has the main cylinder on it. The said gas distributing machanism is perfect, reliable, small and flexible in design and mounting.
Description
The invention belongs to four stroke engine valve timing technical field, mainly propose a kind of eccentric wheel, cammingly hydraulic valve mechanism of four stroke engine.
Timing of engine mechanism in using now all adopts the camshaft that engine crankshaft is slowed down at 2: 1 to drive a cover complex mechanical construction control valve opening mechanism such as rocking arm, tappet and finishes distribution work, according to the change in location between camshaft and the rocking arm, the form that present valve mechanism mainly adopts is; The underneath type cam, overhead cam and underneath type cam are by hydraulic tappet transmission etc., above structure is the present conventional operation technique of motor, existing four stroke engine is because the mechanical transmission position is specific, rocking arm, tappet etc. that make to open valve can not be distributed in a slice cam around and can only adopt the form of multi-disc camshaft, thereby make the difficulty of processing of camshaft increase; Because not malleable is fixed in being provided with of mechanical location, generally have only purposes to design valve-opening times by different operating modes according to motor, in case determine just no longer to change, so the distribution open phase angle of the four stroke engine of the above valve mechanism of existing employing is different basically, present circumstances is down because the extensive use of high-tech development and electronic technology, adjust control signal though under Under Different Work Condition of Engine, can take out, but because the difficulty that mechanical structure is adjusted is very big, use comparatively difficulty, external at present have and adjust that cam is linear can to become cam etc. according to adjusting the adjustment form of signal to the air gate distribution timing on the minority battle wagon.Above-mentionedly determine that by cam driven rocking arm, tappet the mechanism of valve opening still has the following disadvantages: the camshaft manufacturing process complexity of (1), multi-disc cam, difficulty of processing is big and cost is high; (2), because cam is linear steep, rocking arm is easy to wear, impact force causes the life-span shorter greatly; (3), the gas distribution system relation of being in transmission connection, gap accumulation, the noise big (for the main noise source of motor) of causing easy to wear; (4), that distribution device transmits part is many, and certain volume is arranged, so design and installation is restricted, causes that the motor volume is big, weight is big, cost is higher; (5), valve-opening time restricts by camshaft fully, is difficult for changing port timing accordingly with working conditions change, cam wear will cause timing to change in addition, reduces distribution efficient.Existing in addition mechanism is not easy to be provided with many valve mechanisms.
The purpose that the present invention proposes promptly is to change existing cam rocker arm formula mechanical mechanism, a kind of eccentric wheel (cam) formula hydraulic valve mechanism is proposed, adjust thereby the distribution control reliability is improved and be easy to, and make it have that structure is comparatively simple, the free characteristics easily of design and installation, its volume and weight all further rationally is suitable for, and obtains working life prolonging.
The present invention finishes the technological scheme that its above-mentioned task takes; With engine crankshaft 2: the 1 coaxial eccentric wheel that is provided with on the big positive hour wheel of transmitting that slows down, setting is by master cylinder and pay the hydraulic valve mechanism with microcirculation function and internal oil passages degassing function that oil cylinder constitutes, wherein the main plunger of master cylinder is arranged on the periphery, radial plane of eccentric wheel or cam, shaft axis passes eccentric rotating center, set the timing drain charge hole that control valve opening position is used on casing wall between the main plunger lower dead center of master cylinder and the top dead center, the drain charge oil duct in timing drain charge hole is communicated with oil storage pool; In order to rotate at eccentric wheel specific angle be valve need begin to open the time main plunger top concordant with timing drain charge hole and can just seal timing drain charge hole, paying on the oil cylinder casing wall of valve stem and valve spring is housed sets the overflow hole that communicates with oil storage pool by oil circuit, paying oil cylinder plunger payable at sight plunger is connected with valve stem, it is concordant with overflow hole and make overflow hole begin overflow to pay the plunger upper end during to maximum opening at valve, is correspondingly provided with the compensation oil duct with one-way valve that the hydraulic oil that loses in the oil circuit is compensated.
Its driving to the master cylinder plunger also can be finished by cam, promptly takes cam to replace eccentric wheel.
When its linear time that makes the main plunger setting in motion of the cam that adopts in advance in valve during by opening time of port timing requirement, even being in, also specific valve adopts the oil circuit that on the top dead center of main plunger and the master cylinder casing wall between the lower dead center, sets timing drain charge hole when the outer profile curve that is fully closed to this section cam that acts on main plunger in the unlatching during this period of time has the outer profile curve of reducing with respect to rotating center, so that principal post is plugged with one section idle stroke, utilize the drain charge effect in timing drain charge hole to adjust air gate distribution time and position.
When its line style of cam that adopts make time of main plunger setting in motion and valve by opening time of port timing requirement at once, also be specific valve when being in the relative rotating center of outer profile curve that is fully closed to this section cam that acts on main plunger in beginning to open during this period of time for isometrical outer profile curve the master cylinder casing wall be enclosed construction, promptly adopt the oil circuit that does not set timing drain charge hole.
For further improving the adjustability of distribution valve timing, adjustment valve timing dish can be set, its with eccentric wheel, the concentric installation of cam and can relative eccentric wheel, the cam rotation several angle, the master cylinder device is on timing adjustment dish, make adjustment valve timing coil relative eccentric wheel, cam sense of rotation promptly forward or reversely turn over a specific angle, the axis of main plunger was changed with the time that eccentric wheel, cam peak radial line overlap, thereby change the distribution time of opening valve.
According to engine working process, in the periphery, radial plane of eccentric wheel or cam according to inlet and outlet time requirement suitably angle set gradually one or more master cylinders, make valve opening and close to drive corresponding pair of oil cylinder plunger action respectively, carry out air inlet, exhaust.
An eccentric wheel, cam can be set, also can coaxially at a certain angle be arranged side by side a plurality of eccentric wheels, cam.
Can one or more adjustment valve timing dishes be set with eccentric wheel, cam are concentric.
Can on a timing adjustment dish, the valve job order by motor one or more master cylinders be set with different amount.
Can dispose one or more pairs of oil cylinders with a master cylinder, the main plunger action can drive a plurality of pairs simultaneously and live valve air inlet simultaneously or the exhausts that a plurality of identical functions are controlled in the plug action.
Can or promote a plurality of valve stem work simultaneously by one of one pair of plunger promotion, reach the valve air inlet simultaneously or the exhaust of a plurality of identical functions.
Valve mechanism of the present invention has following characteristics;
(1), the present invention adopts eccentric wheel, cam-actuated hydraulic transmission air valve mechanism, by adjusting the relative position of eccentric wheel, cam and valve main plunger, adopt eccentric wheel, cam and timing hole, overflow hole to mate control simultaneously, make gas distribution structure more perfect, reliable, and the timing adjustability of valve mechanism is improved.
2, eccentric wheel, cam fluid drive mechanism make that a slice eccentric wheel or cam are that may command is organized valve more, and structure is comparatively simple and reliable, has reduced integrally-built volume and weight, and design and installation freely makes things convenient for, and have reduced manufacturing cost and use cost.
(3), its structural design reduced the useless power loss and the wearing and tearing of existing valve mechanism, prolonged the working life of distribution device and reduced the workload of maintaining.
(4), can develop many valves easily, can open and close with the valve of main piston control identical function more than two and two according to hydraulic transfering principle, adapt to the hyperpneustic development trend of development.
(5), since in the hydraulic pressure transfer process liquid regularly circulate, reduced that liquid does not circulate and the pneumatosis phenomenon that produces, make valve can be under bad working environment (high temperature, high frequency, at a high speed) can both work reliably.
The embodiment of the invention provides the following drawings;
Accompanying drawing 1 is the embodiment of the invention 1 structural representation.
Accompanying drawing 2,3,4 is a distribution device working procedure schematic representation.
Accompanying drawing 5 is configured into the schematic representation of exhaust valve for single cylinder.
Accompanying drawing 6 has the schematic representation of two cover inlet and exhaust valves for single cylinder.
Accompanying drawing 7 has another schematic representation of two cover inlet and exhaust valves for single cylinder.
The schematic representation that master cylinder was provided with when accompanying drawing 8 was multicylinder engine.
Accompanying drawing 9 is embodiment's 2 structural representations.
Embodiment 1:
Structure as shown in Figure 1: little positive hour wheel 2 is contained on the output shaft of bent axle 3, link to each other with big positive hour wheel 1, little positive hour wheel 2 is 1: 2 with the gear ratio of big positive hour wheel 1, eccentric wheel 28 is contained on the same axle with big positive hour wheel 1, adjustment valve timing dish 29 and the concentric greatly just hour wheel periphery that is arranged on of eccentric wheel, and can rotate to an angle around eccentric wheel center " O ", master cylinder 23 devices its shaft axis on adjustment valve timing dish 29 passes the eccentric wheel rotating center, can be on adjustment valve timing dish according to the master cylinder of engine cylinder number situation dress proper number, also a plurality of timing adjustment dishes can be installed side by side with one heart, main plunger 27 fits tightly with eccentric wheel under return spring 26 effects, set the timing drain charge hole 25 that control valve opening position is used on the master cylinder casing wall between main plunger 27 lower dead center and the top dead center, the drain charge oil duct 22 in timing drain charge hole 25 links to each other with oil sump 24, in order to being that valve is not when beginning to open making eccentric wheel not rotate to special position, what the rotation of eccentric wheel this moment made main plunger makes pressure oil release to oil storage pool 24 from timing drain charge hole to top offset, and do not cause 13 actions of pair plunger to make valve begin to open, according to four stroke engine distribution principle, valve just begins to open when eccentric wheel rotates to a specific angle, promptly under this angle, make main plunger 27 tops concordant with timing drain charge hole and can be just with its sealing, master cylinder 23 tops link to each other with pair oil cylinder 14 upper ends through working connection 17, pay in the oil cylinder 14 valve stem 9 is housed, valve spring 12, valve stem 9 is connected with a pair plunger 13, pay on the oil cylinder casing wall and set the overflow hole 16 that communicates with oil storage pool, pay at valve that the plunger upper end is concordant with overflow hole to make overflow hole begin overflow during to maximum opening, its effect is when a pair plunger goes downwards to the required maximum opening of valve, pressure oil to overflow hole is spilled over to oil storage pool, pay plunger 13 and valve return springs 12 and reach balance during this time, the corresponding compensation oil duct 20 that between oil circuit and oil storage pool 24, is provided with one-way valve 19, make one-way valve 19 open the hydraulic oil that in oil circuit, replenishes to fall in order to the negative pressure that in the returning place force effect lower pipeline of main plunger, forms by timing drain charge hole 25 and overflow hole 16 earial drainages, because it is main, pay oil suction → oil spilling effect that plunger produces, make oil circuit produce a kind of micro circulation (not circulating when opening valve during proper functioning), reduced and deposited gas, hydraulic circuit of the every action of as many as valve has just carried out an exhaust.
Because the earial drainage of overflow hole, lost a part of hydraulic oil in the oil circuit, when main plunger goes downwards to certain position, (pay plunger and go upward to solstice), in returning place force effect lower pipeline, must form certain negative pressure, one-way valve 19 was had an effect and was compensated oil duct 20 additional hydraulic oil that leaks away in oil circuit this moment, thereby make main plunger descending smoothly, when main plunger walks to main timing hole, one-way valve 19 is ineffective, directly replenish hydraulic oil and change from oil storage pool 24 by timing drain charge hole, make the main plunger return more reliable, and get ready for the next one circulates.
Only provide the structural representation of a valve job in the accompanying drawing 1, the positive hour wheel 1,2 of size, crank 3, connecting rod 4, piston 5, cylinder body 6, firing chamber 8, cylinder head 10, spark plug 11 are the structure of available engine cylinder body among the figure, identical with the available engine housing structure, do not change.
Structure shown in accompanying drawing 2,3,4, to mate the explanation of control unlatching valve timing simultaneously by eccentric wheel 28, timing drain charge hole 25, overflow hole 16:
Establish by eccentric wheel 28 rotating center O as figure and to make ray OY ' along least radius, main plunger 27 shaft axis Y are by the eccentric wheel rotating center, angle is 0 ° when two lines overlap, behind eccentric wheel 28 rotation β angles, its main plunger produces △ Y displacement along being driven by eccentric wheel on its direction of axis line, △ Y has frequently in the eccentric wheel rotary course increases or minimizing trend, a △ Y value and its variation tendency have promptly been determined in every as we know from the figure given β angle, according to four stroke engine distribution principle, provide eccentric wheel 28 when forwarding a certain degree α to, valve just begins to open, promptly if under this angle, make main plunger 27 tops concordant with 25 positions, timing drain charge hole and can just seal the time (this moment, △ Y must have increase trend) can reach the action of opening valve by design, in like manner, also can design the valve of paying oil cylinder pays plunger and begins earial drainage when eccentric wheel rotates to several angle, valve no longer continues to open (remaining on the certain position), when continuing to rotate to eccentric wheel or cam (symmetry axis) OY ' and overlap with shaft axis OY, (this moment the position be the main plunger peak when △ Y has just had the trend of reducing then valve under the returning place force effect, begin closedly, eccentric wheel or cam continue to rotate just makes valve reach the purpose of complete closure gradually.
If its angle is α when valve is just closed fully
2, α then
2-α
1=α is air inlet or exhaust distribution angle, and this angle comprehensively forms with main plunger aperture position and pair plunger and main plunger diameter ratio.
Rotation speed change according to engine operating condition or motor, port timing also needs corresponding change, can make 29 relative eccentric wheel 28 rotations of timing adjustment dish be reverse or forward turn over a corresponding angle α of variation, thereby the axis of main plunger and the time that eccentric wheel peak radial line overlaps are changed, thereby change the distribution time of opening valve, timing adjustment dish is fixed after can once adjusting, and also can be accessed control signal and be adjusted valve timing in good time by motor by the engine operating condition requirement.
The device mode of its air gate distribution timing adjustment dish: at first by existing four stroke engine distribution principle, master cylinder is fixed on the air gate distribution adjustment dish with certain angle mutually, the main plunger shaft axis intersects with the rotating center axis of valve timing adjustment dish and is vertical, and each main plunger shaft axis is in the same plane, during device with this overall fixed (or claim body) in eccentric support, formed plane of its shaft axis of master cylinder and eccentric radial plane are overlapped and both rotating centers coincidences, its means of fixation can adopt chute that the guiding groove of circumferencial direction is promptly arranged on the adjustment dish, or recessed circular groove arranged on the support, the adjustment dish has the cylindrical casing etc. of projection, make distribution adjustment dish relatively eccentric wheel rotate to an angle.
Accompanying drawing 5 provides that each cylinder one packs into, the signal during exhaust valve: can adopt an eccentric wheel 28, each work of intake valve and exhaust valve characteristics once when circling according to motor revolution two all eccentric wheels 28, be arranged in the master cylinder of inlet and outlet door in the eccentric wheel same plane on every side successively in proper order, and make the main plunger axis all by the eccentric wheel rotating center, then OY ' has formed different angles with each plunger axle center line, valve just can open and close successively by the time that designs, accompanying drawing signal be a valve in operating position, a valve is at open position.
Two eccentric wheels also can be set, and soon the inlet and outlet eccentric wheel will be coaxial at a certain angle is arranged side by side, and the main shaft plug action that drives respectively separately drives a pair plunger action, can open and close valve successively by the time that designs equally.
Accompanying drawing 6,7 provides the signal that each cylinder of motor has two or more identical function valves, can drive two or more valve stem work simultaneously by paying the oil cylinder plunger, payable at sight plunger 13 drives two valve stems by rocking arm tappet 32 and works simultaneously, wherein 31 is pitman arm shaft, and 30 is rocking arm.Reach the valve air inlet simultaneously of identical function more than two, the purpose of exhaust, also can be by two or more pairs of oil cylinders of a master cylinder configuration, each is paid oil cylinder and promotes a valve stem job, and the main plunger action drives valve close synchronously or the unlatching that two or more pairs plunger action is controlled identical function simultaneously.
The signal that master cylinder was provided with when accompanying drawing 8 provided a plurality of cylinder body; Identical during with single cylinder, can with the master cylinder of all valves of all cylinders all on demand order and the angle of regulation arrange, can form the purpose of the many groups of an eccentric wheel control valve, provide a kind of form of arranging 4 valves respectively among the figure, be the main plunger of 4 valves of two cylinder, they can drive the purpose that corresponding valve reaches engine operation in order respectively.
Can certainly adopt by required angle is coaxial and be arranged side by side a plurality of eccentric wheels, the same manner is provided with several master cylinders and main plunger in periphery, eccentric radial plane simultaneously by required angle and drives a plurality of valves and reach the purpose that makes engine operation.
Eccentric wheel in the said structure can take cam to replace, and is identical when its valve control machanism adopts eccentric wheel together; When time that its line style of cam that adopts makes the main plunger setting in motion in advance in the opening time of valve by port timing requirements, also be that specific valve is in to be fully closed to and still adopts the oil circuit that sets timing drain charge hole on the top dead center of main plunger and the master cylinder casing wall between the lower dead center when relative its rotating center of outer profile curve that acts on this section cam of main plunger in beginning to open during this period of time has the outer profile curve of reducing.
When adopting eccentric wheel and above-mentioned cam structure, returning place force as if main plunger when the downward return of main plunger is stronger, when being returning place force greater than the negative pressure that produces in the oil circuit, can make main plunger arrive timing drain charge hole, at this moment can all change to suck by the hydraulic oil of timing drain charge hole and overflow hole loss and be replenished by timing drain charge hole and oil duct, at this moment main plunger can be got back to minimum point smoothly and prepare to open the process of valve next time, and one-way valve compensation oil circuit can be set in this case.
Accompanying drawing 9 provides the another kind of structural type when adopting cam structure: when cam 28 its line styles that adopt make time of main plunger 27 setting in motions and valve by opening time of port timing requirement fully at once, also be specific valve be in be fully closed to this section cam that acts on main plunger in beginning to open during this period of time outer profile curve relatively its rotating center be isometrical outer profile curve, employing does not set the hydraulic valve oil circuit in timing drain charge hole on master cylinder 23 casing walls, promptly the casing wall of master cylinder 23 is an enclosed construction.This structure make main plunger 27 upwards action promptly produce pressure and make and pay plunger action and promote a valve opening air inlet or an exhaust, when camshaft rotates the point of contact of cam 28 and main plunger 27 in a single day arrived shortly past etc. radius arc R place promote upwards action of main plunger, main plunger promptly promotes to pay plunger 13 and opens valve, paying plunger when reaching overflow hole 16 stops descending, overflow also is after cam rotates to peak later, main plunger begins descending under the returning place force effect, pay plunger 13 when just getting back to upper position-arresting because that part of volume that overflow is fallen makes main plunger 27 continue descending generation negative pressure, at this moment one-way valve 19 is opened to oil circuit and is replenished hydraulic oil, touch the bottom until main plunger, cam continues rotation and then begins to open the action of valve next time then.
With eccentric wheel proposed by the invention, the cam principle is identical, also can adopt and big positive coaxial crank-connecting rod, offset connecting rod, the eccentric grove structure of being provided with of hour wheel, all the other hydraulic valve mechanisms are identical with above-mentioned structure, but when adopting these structures, it is comparatively complicated that whole valve distribution mechanism will become, and corresponding its precision, accuracy also certainly will be affected.
Claims (10)
1, a kind of eccentric wheel (cam) formula hydraulic valve mechanism, feature of the present invention is: going up coaxial eccentric wheel, the cam (28) of being provided with engine crankshaft (3) 2: 1 big positive hour wheels of transmitting (1) of slowing down, setting is by master cylinder (23) and pay the hydraulic valve mechanism with microcirculation function and internal oil passages degassing function that oil cylinder (14) constitutes, wherein the main plunger (27) of master cylinder (23) is arranged on the periphery, radial plane of eccentric wheel, cam (28), and the shaft axis of main plunger (27) is by the rotating center of eccentric wheel, cam; Paying on oil cylinder (14) casing wall of valve (18) and valve spring (12) is housed set overflow hole (16), paying plunger (13) is connected with valve stem (9), it is concordant with overflow hole (16) and make overflow hole (16) begin overflow to pay plunger (13) upper end during to maximum opening at valve, and oil circuit is provided with the compensation oil duct (20) with one-way valve (19) that hydraulic oil that earial drainage is fallen compensates.
2, eccentric wheel (cam) formula hydraulic valve mechanism according to claim 1, it is characterized in that: set the timing drain charge hole (25) that control valve opening position is used when adopting eccentric wheel on master cylinder (23) casing wall, the drain charge oil duct in timing drain charge hole (25) is communicated with oil storage pool (24).
3, eccentric wheel (cam) formula hydraulic valve mechanism according to claim 1 is characterized in that; When time that its line style of cam that adopts makes main plunger (27) setting in motion in advance in valve during by opening time of port timing requirement, also be specific valve when being in the outer profile curve that is fully closed to this section cam (28) that acts on main plunger (27) in beginning to open during this period of time its rotating center having the outer profile curve of reducing relatively, set the timing drain charge hole (25) that control valve opening position is used on master cylinder (23) casing wall.
4, eccentric wheel (cam) formula hydraulic valve mechanism according to claim 1, it is characterized in that: when its line style of cam that adopts make time of main plunger (27) setting in motion and valve by opening time of port timing requirement fully at once, also be specific valve when being in the outer profile curve that is fully closed to this section cam (28) that acts on main plunger (27) in beginning to open during this period of time its rotating center is for isometrical outer profile curve relatively, the casing wall of master cylinder (23) is an enclosed construction.
5, according to claim 1 or 2 or 3 or 4 described eccentric wheel (cam) formula hydraulic valve mechanisms, it is characterized in that: can set gradually one or more master cylinders (23) according to inlet and outlet time requirement with suitable angle in the periphery, radial plane of eccentric wheel, cam (28), to drive corresponding pair of oil cylinder (14) plunger (13) action respectively valve opening is closed, carry out exhaust or air inlet.
6, according to claim 1 or 2 or 3 or 4 described eccentric wheel (cam) formula hydraulic valve mechanisms, it is characterized in that; Can be provided with adjustment valve timing dish (29), it can be one and also can be a plurality of of concentric setting, its with eccentric wheel, the concentric installation of cam (28) and can relative eccentric wheel, cam (28) rotates to an angle, master cylinder (23) is arranged on the adjustment valve timing dish (29), eccentric wheel, cam (28) turn an angle relatively by adjustment valve timing dish (29), the axis of main plunger (27) was changed with the time that eccentric wheel, cam (28) peak radial line overlap, thereby adjust the distribution time of opening valve.
7, according to claim 1 or 2 or 3 or 4 described eccentric wheel, (cam) formula hydraulic valve mechanisms, it is characterized in that: can coaxially at a certain angle be arranged side by side two or more eccentric wheels or cam (28).
8, according to claim 1 or 2 or 3 or 4 described eccentric wheel, (cam) formula hydraulic valve mechanisms, it is characterized in that: can pay plunger (13) by one and promote two or more valve stems (9) work simultaneously, make the valve air inlet simultaneously or the exhaust of two or more identical functions.
9, according to claim 1 or 2 or 3 or 4 described eccentric wheel, (cam) formula hydraulic valve mechanisms, it is characterized in that; Can dispose two or more pairs of oil cylinders (14) by a master cylinder (23), main plunger (27) action drives the valve air inlet simultaneously or the exhaust of two or more identical functions of two or more pairs of plungers (13) action control simultaneously.
10, according to claim 1 or 2 or 3 or 4 described eccentric wheel (cam) formula hydraulic valve mechanisms, it is characterized in that: when negative pressure that the returning place force of main plunger (27) produces in greater than working connection, can replenish hydraulic oil to working connection (17) by timing drain charge hole (25) and the compensation oil duct (20) that its oil duct that is communicated with oil storage pool (24) is replaced one-way valve (19).
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN95107511A CN1139178A (en) | 1995-06-23 | 1995-06-23 | Eccentric-wheel (cam) hydraulic air gate mechanism |
| AU61867/96A AU6186796A (en) | 1995-06-23 | 1996-06-24 | A hydraulic driving valve device |
| PCT/CN1996/000047 WO1997001022A1 (en) | 1995-06-23 | 1996-06-24 | A hydraulic driving valve device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN95107511A CN1139178A (en) | 1995-06-23 | 1995-06-23 | Eccentric-wheel (cam) hydraulic air gate mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1139178A true CN1139178A (en) | 1997-01-01 |
Family
ID=5076361
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95107511A Pending CN1139178A (en) | 1995-06-23 | 1995-06-23 | Eccentric-wheel (cam) hydraulic air gate mechanism |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN1139178A (en) |
| AU (1) | AU6186796A (en) |
| WO (1) | WO1997001022A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102777225A (en) * | 2012-08-09 | 2012-11-14 | 杭州电子科技大学 | Controllable valve mechanism and valve timing adjustment method |
| CN104405468A (en) * | 2014-09-30 | 2015-03-11 | 刘恩均 | Hydraulic valve opening/closing device of engine |
| CN108240244A (en) * | 2017-12-29 | 2018-07-03 | 潍柴动力股份有限公司 | Diesel engine inlet valve variable system and diesel engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108661785B (en) * | 2018-07-26 | 2024-01-23 | 谭建文 | Crankless rotary Atkinson cycle engine |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2448311B2 (en) * | 1974-10-10 | 1978-03-23 | Maschinenfabrik Augsburg-Nuernberg Ag, 8500 Nuernberg | Adjustable hydraulic valve control for reciprocating piston engines or machines |
| DE3115424A1 (en) * | 1981-04-16 | 1982-11-11 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg | DEVICE FOR ACTUALLY ACTUATING GAS EXCHANGE VALVES |
| JPS59229012A (en) * | 1983-06-08 | 1984-12-22 | Yanmar Diesel Engine Co Ltd | Valve operating mechanism of internal-combustion engine |
| DE3504639A1 (en) * | 1985-02-11 | 1986-08-14 | INTERATOM GmbH, 5060 Bergisch Gladbach | HYDRAULIC CONTROL FOR VALVES OF INTERNAL COMBUSTION ENGINES |
| JP2580711B2 (en) * | 1988-05-23 | 1997-02-12 | トヨタ自動車株式会社 | Valve drive for internal combustion engine |
| DE3939066A1 (en) * | 1989-11-25 | 1991-05-29 | Bosch Gmbh Robert | ELECTROHYDRAULIC VALVE CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINES |
-
1995
- 1995-06-23 CN CN95107511A patent/CN1139178A/en active Pending
-
1996
- 1996-06-24 AU AU61867/96A patent/AU6186796A/en not_active Abandoned
- 1996-06-24 WO PCT/CN1996/000047 patent/WO1997001022A1/en active Application Filing
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102777225A (en) * | 2012-08-09 | 2012-11-14 | 杭州电子科技大学 | Controllable valve mechanism and valve timing adjustment method |
| CN104405468A (en) * | 2014-09-30 | 2015-03-11 | 刘恩均 | Hydraulic valve opening/closing device of engine |
| CN108240244A (en) * | 2017-12-29 | 2018-07-03 | 潍柴动力股份有限公司 | Diesel engine inlet valve variable system and diesel engine |
| CN108240244B (en) * | 2017-12-29 | 2023-12-19 | 潍柴动力股份有限公司 | Variable system of diesel engine inlet valve and diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO1997001022A1 (en) | 1997-01-09 |
| AU6186796A (en) | 1997-01-22 |
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