CN205578058U - Full variable valve's of hydraulic drive formula mechanical regulating unit - Google Patents
Full variable valve's of hydraulic drive formula mechanical regulating unit Download PDFInfo
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- CN205578058U CN205578058U CN201620348185.XU CN201620348185U CN205578058U CN 205578058 U CN205578058 U CN 205578058U CN 201620348185 U CN201620348185 U CN 201620348185U CN 205578058 U CN205578058 U CN 205578058U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The utility model provides a full variable valve's of hydraulic drive formula mechanical regulating unit belongs to the engine technology field, the utility model discloses a two guide rails of base are arranged respectively in to two plungers of two valve open and close adjustment mechanisms, two plunger tops contact two cams respectively, among the induction stroke: the helicla flute I of plunger I and the oil duct I of base and II intercommunications of oil duct, helicla flute II communicates with oil duct IV with the oil duct II of base in the plunger II, among the exhaust stroke: the helicla flute III of plunger II and the oil duct III of base and V intercommunications of oil duct, adjustment mechanism was supplied with to the inlet port of hydraulic piston valve group, the draining hole of hydraulic piston valve group, hydraulic oil oil pipe II respectively with the oil duct of base IV, I intercommunication of oil duct V and oil duct, the utility model discloses can realize that valve lift, valve timing are variable in succession, can during a certain period keep the high lift of valve, can realize that the gasoline engine does not have the air throttle load control, does not reduce pumping loss, improve the charging efficiency to realize miller cycle, reach energy saving and emission reduction's effect, simple structure, easily control.
Description
Technical field
This utility model belongs to technical field of engines, is specifically related to a kind of hydraulic drive type combustion engine mechanical and regulates full changeable air valve
Mechanism.
Background technology
The valve actuating mechanism of conventional engines, owing to structure is fixed, in engine operation process, port timing is unalterable,
It is typically only capable to ensure the performance at a certain operation optimization internal combustion engine, it is impossible to take into account the requirement of each operating mode simultaneously, be extremely difficult to real
Optimal port timing.These fixing valve operational factors are that internal combustion engine runs require valve operation each under different operating modes
The one planting comprehensive contradiction is traded off.Therefore, in order to meet port timing demand different under different operating mode, internal combustion engine economy is improved
Property and dynamic property, reduce hazardous emission, need use changeable air valve technology.Changeable air valve technology can be according to engine conditions
Change, it is achieved valve stroke is from zero to design maximum lift and the continuous variable of port timing.
Owing to changeable air valve technology has huge superiority, it has become as a focus direction of Current internal combustion engines research, state
More inside and outside institution of higher learning and scientific research institution expand the research work to variable valve actuator for air in succession.Although changeable air valve machine at present
Structure of a great variety, operation principle is also not quite similar, but hydraulic-driven variable valve actuator for air can realize valve stroke and distribution
The flexible control of phase place, and paid close attention to by all big enterprises.At present, the implementation that hydraulic-driven changeable air valve is common has
Two kinds: a kind of is the variable valve system of electric-liquid type without returning spring with Ford company hydraulic valve drive mechanism as representative, its bag
Include high pressure, low pressure accumulator, and the plunger of a two-sided effect be installed at valve top, plunger upper part can with high pressure fuel source and
Low pressure oil sources is connected, and bottom is connected with high pressure fuel source, by the open and close of two electromagnetic valve oil circuit controls so that on plunger
Portion is different from bottom oil pressure, produces pressure differential, and then realizes the opening and closing of valve；Another kind is public with Daimler-Benz
Department dual spring hydraulic-driven variable valve actuator for air be representative have returning spring electric-liquid type variable valve system, this system is by hydraulic pressure system
System, plunger valve body, back-moving spring, solenoid electric valve etc. form, and control hydraulic oil by electromagnetic valve and produce plunger valve body
Pressure, the open and close of the co-controlling valve of making a concerted effort of plunger valve body pressure and spring force.The wherein system of Ford company
It is completely dependent on liquid potential energy at work and valve kinetic energy mutually converts, control pressure fluid flowing and internal combustion engine with solenoid
Valve opening and closedown, maximum problem is that solenoid will consume excessive power, and does not has good response, durability
And reliability.Although and the system of Daimler-Benz company using dual spring solve solenoid to a certain extent and consumed energy
Many problems, but when internal combustion engine runs up, electromagnetic valve response speed cannot meet requirement equally.This shows current liquid
The subject matter that pressure drives changeable air valve to popularize is electromagnetic valve power consumption height, and the market price is expensive, and response speed cannot meet
Demand, durability and the reliability of valve body work have much room for improvement.
Summary of the invention
The purpose of this utility model is to overcome the power consumption of existing hydraulic-driven variable valve actuator for air electromagnetic valve high and high-speed response,
Durability, reliability can not meet demand and the shortcoming such as expensive, it is provided that a kind of simple and reliable for structure and can control valve flexibly
The mechanic adjustment unit of the full changeable air valve of fluid pressure type of lift and port timing.
This utility model by valve opening and closing governor motion I A, base B, valve opening and closing governor motion II C, hydraulic piston valve group D,
Hydraulic oil supply governor motion E, bolt I 1, cam I 2, bolt II 3, cam II 4 and fuel tank II 5 composition, wherein valve
The plunger I G top of opening and closing governor motion I A contacts with cam I 2；Plunger I G of valve opening and closing governor motion I A is placed in the end
In the guide rail I 17 of seat B, and the boss II 14 of plunger I G is slidably connected with guide rail I 17, valve opening and closing governor motion I A's
Spring I 6 lower end is spacing by guide rail I 17 lower end；Location-plate I 7 warp of turbine axle sleeve I F in valve opening and closing governor motion I A
Bolt I 1 is affixed with the bolt hole I 16 of base B；The helicla flute of plunger I G in valve opening and closing governor motion I A in induction stroke
I 13 connect with oil duct I 24 and the oil duct II 18 of base B；The plunger II I top of valve opening and closing governor motion II C and cam
II 4 contacts；The plunger II I of valve opening and closing governor motion II C is placed in the guide rail II 20 of base B, and the boss of plunger II I
IV 33 guide rails II 20 are slidably connected, and spring II 25 lower end of valve opening and closing governor motion II C is spacing by guide rail II 20 lower end；Gas
In door opening and closing governor motion II C, the location-plate II 26 of turbine shaft sleeve II H is affixed with the bolt hole II 19 of base B through bolt II 3；
The oil duct II 18 of helicla flute II 32 and base B and oil duct IV 21 in plunger II I in valve opening and closing governor motion II C in induction stroke
Connection；The oil duct III 23 of helicla flute III 34 and base B and oil in plunger II I in valve opening and closing governor motion II C in exhaust stroke
Road V 22 connects；The fuel feed hole 36 of hydraulic piston valve group D is connected with the oil duct IV 21 of base B through conduit；Hydraulic piston gas
The oil leak hole 44 of door group D is connected with the oil duct V 22 of base B through conduit；The oil pipe II 51 of hydraulic oil supply governor motion E with
Oil duct I 24 connection of base B.
Described valve opening and closing governor motion I A is by turbine axle sleeve I F, plunger I G, spring I 6, location-plate I 7 and regulation snail
Bar I 8 forms, and wherein turbine axle sleeve I F is provided with chassis I 9, centre bore I 10 and turbine I 11；Plunger I G top is provided with
Boss I 12, plunger I G bottom is provided with boss II 14, and plunger I G bottom is provided with nose bar I 15；Helicla flute I 13 is located at boss
II 14 tops；Spring I 6 is placed on the nose bar I 15 of plunger I G；The turbine I 11 that regulation worm screw I 8 is placed in turbine axle sleeve I F is left
End；Location-plate I 7 is pressed on the chassis I 9 of turbine axle sleeve I F；The centre bore I 10 of turbine axle sleeve I F and the boss of plunger I G
I 12 spline gaps connect.
Described base B left part is provided with guide rail I 17；Base B right part is provided with plunger guide rail II 20；The left portion of plunger guide rail I 17
It is provided with oil duct I 24, and oil duct I 24 is opened on base B left surface；Plunger guide rail I 17 upper right quarter and guide rail II 20 upper left quarter
The oil duct II 18 being communicated with；Plunger guide rail II 20 lower left quarter is provided with oil duct III 23, and oil duct III 23 is opened on base B bottom surface；
Plunger guide rail II 20 upper right quarter is provided with oil duct IV 21, and oil duct IV 21 is opened on base B right flank；Plunger guide rail II 20 bottom right
Portion is provided with oil duct V 22, and oil duct V 22 is opened on base B right flank；Base B upper surface is provided with by plunger guide rail I 17 left side
Bolt hole I 16；Base B upper surface is provided with bolt hole II 19 by plunger guide rail II 20 left side.
Described valve opening and closing governor motion II C is by turbine shaft sleeve II H, plunger II I, spring II 25, location-plate II 26 and regulation
Worm screw II 27 forms, and wherein turbine axle sleeve H is provided with chassis II 28, centre bore II 29 and turbine II 30；Plunger II I top sets
Having boss III 31, plunger II I bottom to be provided with boss IV 33, plunger II I bottom is provided with nose bar II 35；Helicla flute II 32 is located at convex
Platform IV 33 top, helicla flute III 34 is located at boss IV 33 bottom；Spring II 25 is placed on the nose bar II 35 of plunger II I；Regulation snail
Bar II 27 is placed in turbine II 30 left end of turbine shaft sleeve II H；Location-plate II 26 is pressed on the chassis II 28 of turbine shaft sleeve II H；Turbine
The centre bore II 29 of shaft sleeve II H is connected with boss III 31 spline gaps of plunger II I.
Described hydraulic piston valve group D is made up of piston bush 37, valve 39, spring base 40, spring III 41 and piston 42,
Wherein piston bush 37 upper left wall is provided with oil leak hole 44, and piston bush 37 top is provided with fuel feed hole 36；Piston 42 is placed in piston bush 37
In, and be slidably connected with piston bush 37 inwall；Plunger shaft 43 is the chamber portion between piston 42 top and piston bush 37；
Valve 39 bottom is connected with spring base 40, is cased with spring III 41 in the middle part of valve 39, and valve 39 upper end passes bottom piston bush 37
Centre bore III 38, affixed with piston 42 lower end, spring III 41 upper end by spacing bottom piston bush 37, spring III 41 lower end by
Spring base 40 is spacing.
Described hydraulic oil supply governor motion E is by electronics air relief valve 45, oil pipe III 46 oil pipe I 47, fuel tank I 48, filtering
Device 49, oil pump 50 and oil pipe II 51 composition, oil pump 50 lower end is connected with cleaner 49 upper end, oil pump 50 upper end and oil pipe
II 51 lower ends connect, and cleaner 49 lower end is connected with fuel tank I 48, and oil pipe I 47 entrance is placed in fuel tank I 48, oil pipe I 47
Outlet is connected with cleaner 49 upper end；Being provided with electronics air relief valve 45 in the middle part of oil pipe III 46, oil pipe III 46 left end is with oil pipe II 51 even
Logical, oil pipe III 46 outlet is placed in fuel tank I 48.
This utility model can be divided into lift control system and timing control system according to control system, and lift control system is hydraulic oil
Supply governor motion E, timing control system includes valve opening and closing governor motion I A, valve opening and closing governor motion II C and base B.
Valve-open phase control process:
When cam I 2 drives plunger I G of valve opening and closing governor motion I A descending, and cam II 4 drives valve opening and closing governor motion
Plunger II I of II C is up, in valve opening and closing governor motion I A the helicla flute I 13 of plunger I G and the oil duct I 24 of base B and
Oil duct II 18 connects, the helicla flute II 32 of plunger II I and the oil duct II 18 of base B and oil duct in valve opening and closing governor motion II C
IV 21 connections, and the helicla flute III 34 of plunger II I and the oil duct III 23 of base B and oil duct in valve opening and closing governor motion II C
V 22 do not connect, and hydraulic oil is pumped into electronics air relief valve 45 by oil pump 50 from fuel tank I 48 after cleaner 49 filters, and passes through
After electronics air relief valve 45 voltage stabilizing flow into oil pipe II 51, then by oil duct I 24, helicla flute I 13, oil duct II 18, helicla flute II 32,
Oil duct IV 21, fuel feed hole 36 flow into plunger shaft 43, and then promote the piston 42 of hydraulic piston valve group D to overcome spring III 41 to push away
Door 39 of taking offence is opened: as it is shown in figure 1, regulation worm screw I 8 drives plunger I G to rotate to a direction by turbine axle sleeve I F,
Helicla flute I 13 on plunger I G also rotates with, and makes the relative position change that helicla flute I 13 exports with oil duct I 24, and then
Making helicla flute I 13 delayed with the moment that oil duct I 24 connects, the time that hydraulic oil flows into plunger shaft 43 through timing control system pushes away
Late, final valve 39 is opened evening；Regulation worm screw I 8 drives plunger I G to rotate to other direction by turbine axle sleeve I F, plunger
Helicla flute I 13 on I G also rotates with, and makes the relative position change that helicla flute I 13 exports with oil duct I 24, and then makes spiral shell
The moment that spin slot I 13 connects with oil duct I 24, hydraulic oil flowed into the time advance of plunger shaft 43 through timing control system in advance,
Final valve 39 is early opened.
Valve-closing phase controlling process:
When cam I 2 drives plunger I G of valve opening and closing governor motion I A up, and cam II 4 drives valve opening and closing governor motion
Plunger II I of II C is descending, in valve opening and closing governor motion I A the helicla flute I 13 of plunger I G and the oil duct I 24 of base B and
Oil duct II 18 does not connects, the helicla flute II 32 of plunger II I and the oil duct II 18 of base B and oil in valve opening and closing governor motion II C
Road IV 21 does not connects, hydraulic oil cannot cleaner 49, oil pump 50, electronics air relief valve 45, oil inlet pipe II 51, oil duct I 24,
Helicla flute I 13, helicla flute I 13, oil duct II 18, helicla flute II 32, oil duct IV 21, fuel feed hole 36 and plunger shaft 43 are formed
Path, and in valve opening and closing governor motion II C, the helicla flute III 34 of plunger II I connects with the oil duct III 23 of base B and oil duct V 22
Logical, make the hydraulic oil in original plunger shaft 43 flow into oil by oil leak hole 44, oil duct V 22, helicla flute III 34, oil duct III 23
Case II 5, completes the draining process of plunger shaft 43, and valve 39 is return under the effect of spring III 41, when valve 39 is taken a seat,
Complete valve 39 to close: as it is shown in figure 1, regulation worm screw II 27 drives plunger II I to rotate by turbine shaft sleeve II H, plunger
Helicla flute III 34 on II I also rotates with, and makes the relative position change that helicla flute III 34 exports, and then spiral with oil duct V 22
Groove III 34 and the time changing of oil duct V 22 UNICOM, hydraulic oil changed the most therewith through the moment of timing control system outflow plunger shaft 43
Becoming, thus regulate valve 39 close moment, finally realizing the IO Intake Valve Opens persistent period controlled also can realize gasoline engine non-air throttle
Spatial load forecasting and Miller cycle.
Liter process control process:
When needing valve 39 high-lift, raise electronics air relief valve 45 pressure；When needing valve 39 little lift, reduce electronics decompression
Valve 45 pressure.
The beneficial effects of the utility model are:
1. can realize the continuous variable of valve stroke, port timing, and valve maximum lift can be kept within a certain period of time.
2. simple in construction, controls flexibly.
3. can realize gasoline engine non-air throttle spatial load forecasting, reduce pumping loss, improve charging efficiency and realize Miller cycle, reaching
Effect to energy-saving and emission-reduction.
Accompanying drawing explanation
Fig. 1 is the structural representation of the mechanic adjustment unit of the full changeable air valve of hydraulic drive type
Fig. 2 is the structural representation of valve opening and closing governor motion I
Fig. 3 is the structural representation of turbine axle sleeve I
Fig. 4 is the structural representation of plunger I
Fig. 5 is the structural representation of base
Fig. 6 is the structural representation of valve opening and closing governor motion II
Fig. 7 is the structural representation of turbine shaft sleeve II
Fig. 8 is the structural representation of plunger II
Fig. 9 is the structural representation of hydraulic piston valve group
Figure 10 is the structural representation of hydraulic oil supply governor motion
Wherein: A. valve opening and closing governor motion I B. base C. valve opening and closing governor motion II D. hydraulic piston valve group
E. hydraulic oil supply governor motion F. turbine axle sleeve I G. plunger I H. turbine shaft sleeve II I. plunger II 1. bolt I
2. cam I 3. bolt II 4. cam II 5. fuel tank II 6. spring I 7. location-plate I 8. regulation worm screw I
9. chassis I 10. centre bore I 11. turbine I 12. boss I 13. helicla flute I 14. boss II 15. nose bar I
16. bolt hole I 17. plunger guide rail I 18. oil duct II 19. bolt hole II 20. plunger guide rail II 21. oil ducts IV
22. oil duct V 23. oil duct III 24. oil duct I 25. spring II 26. location-plate II 27. regulation worm screw II 28. ends
Dish II 29. centre bore II 30. turbine II 31. boss III 32. helicla flute II 33. boss IV 34. helicla flute III
35. nose bar II 36. fuel feed hole 37. piston bush 38. centre bore III 39. valve 40. spring base 41. springs III
42. piston 43. plunger shaft 44. oil leak hole 45. electronics air relief valve 46. oil pipe III 47. oil pipe I 48. fuel tanks
I 49. cleaner 50. oil pump 51. oil pipes II
Detailed description of the invention
Below in conjunction with the accompanying drawings this utility model is described in detail:
Valve opening and closing governor motion I A, base B, valve opening and closing governor motion II C, hydraulic piston valve group D, hydraulic oil supply
Governor motion E, turbine axle sleeve I F, plunger I G, turbine shaft sleeve II H, plunger II I, bolt I 1, cam I 2, bolt II 3,
Cam II 4, fuel tank II 5, spring I 6, location-plate I 7, regulation worm screw I 8, chassis I 9, centre bore I 10, turbine I 11,
Boss I 12, helicla flute I 13, boss II 14, nose bar I 15, bolt hole I 16, plunger guide rail I 17, oil duct II 18, spiral shell
Keyhole II 19, plunger guide rail II 20, oil duct IV 21, oil duct V 22, oil duct III 23, oil duct I 24, spring II 25, location-plate
II 26, regulation worm screw II 27, chassis II 28, centre bore II 29, turbine II 30, boss III 31, helicla flute II 32, boss
IV 33, helicla flute III 34, nose bar II 35, fuel feed hole 36, piston bush 37, centre bore III 38, valve 39, spring base 40,
Spring III 41, piston 42, plunger shaft 43, oil leak hole 44, electronics air relief valve 45, oil pipe III 46, oil pipe I 47, fuel tank
I 48, cleaner 49, oil pump 50, oil pipe II 51 composition.
As shown in Figure 1: bolt I 1 makes location-plate I 7 be clamped on base B, prevent from controlling turbine wheel shaft regulation worm screw I 8
When overlapping I F rotation, loosening occurs in location-plate I 7；Cam I 2 drives plunger I G, it is achieved hydraulic circuit in timing control system
Break-make；Bolt II 3 makes location-plate II 26 be clamped on base B, prevents from controlling the rotation of turbine shaft sleeve II H regulation worm screw II 27
When turning, loosening occurs in location-plate II 26；Cam II 4 drives plunger II I, it is achieved the break-make of hydraulic circuit in timing control system；
Fuel tank II 5 is common fuel tank, is used for storing hydraulic oil；The Main Function of valve opening and closing governor motion I A is whole by regulation
The beginning oil-feed moment of device, and then control the start-up time of valve 39；The Main Function of base B is to provide oil for whole device
Road and position components；The Main Function of valve opening and closing governor motion II C is the beginning draining moment by regulating whole device,
And then control the close moment of valve 39；The Main Function of hydraulic piston valve group D is the unlatching realizing hydraulic control valves 39
With closedown；The Main Function of hydraulic oil supply governor motion E is the lift of regulation valve 39.
As shown in Figure 2: bolt I 1 makes location-plate I 7 be clamped on base B, prevent from controlling turbine wheel shaft regulation worm screw I 8
When overlapping I F rotation, loosening occurs in location-plate I 7；Spring I 6 provides restoring force for plunger I G so that plunger I G is at cam
Can slide up and down in plunger guide rail I 17 under the driving of I 2, and maintain between each part of mechanism normal contact；Location-plate I 7
Limiting the axial location of turbine axle sleeve I F, the two is matched in clearance；Worm screw I 8 engages with turbine axle sleeve I F in regulation, regulates whirlpool
Axle sleeve I F rotates；Turbine axle sleeve I F is connected with plunger I G spline gaps, and turbine axle sleeve I F can drive plunger I G to rotate；
Plunger I G moves reciprocatingly in plunger guide rail I 17.
As shown in Figure 3: be positioned plate I 7 while the shaft core position of chassis I 9 restriction turbine axle sleeve I F and limit axial location；
Centre bore I 10 is connected with boss I 12 spline gaps on plunger I G top；Turbine I 11 engages with regulation worm screw I 8.
As shown in Figure 4: boss I 12 is connected with centre bore I 10 spline gaps of turbine axle sleeve I F；Helicla flute I 13 is by changing
Relative position is exported, thus it is possible to vary the start-up time of valve 39 with oil duct I 24, simple in construction, easy to control；Boss II 14
Top has helicla flute I 13；Nose bar I 15 is that spring I 6 is spacing.
As shown in Figure 5: bolt hole I 16 is used for fixing bolt I 1；Plunger guide rail I 17 mainly provides motion for plunger I G
Guide effect；Oil duct II 18 sets up oil pipe road for device；Bolt hole II 19 is used for fixing bolt II 3；Plunger guide rail II 20 is main
If providing motion guide effect for plunger II I；Oil duct IV 21 sets up oil pipe road for device；Oil duct V 22 is set up logical for device
Oil-piping；Oil duct III 23 sets up oil pipe road for device；Oil duct I 24 sets up oil pipe road for device.
As shown in Figure 6: bolt II 3 makes location-plate II 26 be clamped on base B, prevent from controlling turbine regulation worm screw II 27
When shaft sleeve II H rotates, loosening occurs in location-plate II 26；Spring II 25 provides restoring force for plunger II I so that plunger II I exists
Can slide up and down in plunger guide rail II 35 under the driving of cam II 4, and maintain between each part of mechanism normal contact；Location
Plate II 26 limits the axial location of turbine shaft sleeve II H, and the two is matched in clearance；Worm screw II 27 engages with turbine shaft sleeve II H in regulation,
Regulation turbine shaft sleeve II H rotates；Turbine shaft sleeve II H is connected with plunger II I spline gaps, and turbine shaft sleeve II H can drive plunger II I
Rotate；Plunger II I moves reciprocatingly in plunger guide rail II 20.
As shown in Figure 7: be positioned plate II 26 while the shaft core position of chassis II 28 restriction turbine shaft sleeve II H and limit axial location；
Centre bore II 29 is connected with boss III 31 spline gaps on plunger II I top；Turbine II 30 engages with regulation worm screw II 27.
As shown in Figure 8: boss III 31 is connected with centre bore II 29 spline gaps of turbine shaft sleeve II H；Helicla flute II 32 can realize
Quickly oil-break；Boss IV 33 top has helicla flute II 32, and boss IV 33 bottom has helicla flute III 34；Helicla flute III 34 leads to
Cross change and export relative position with oil duct V 22, thus it is possible to vary the close moment of valve 39, simple in construction, easy to control；Convex
Bar II 35 spring II 25 is spacing.
As shown in Figure 9: the hole that fuel feed hole 36 is opened by piston bush 37 top, its Main Function is to enter piston for hydraulic oil
Chamber 43 provides passage；Piston bush 37 can be that piston 42 motion provides guiding, and piston bush 37 has fuel feed hole 36 and draining
Hole 44；Valve 39 upper end is affixed with piston 42 lower end through the centre bore III 38 of spring base 40 centre bore and piston bush 37；Bullet
Spring abutment 40 is that spring III 41 is spacing；Its Main Function of spring III 41 is to ensure that valve 39 is taken a seat in time, and maintains each part of mechanism
Between normal contact；Valve 39 is promoted to open；Plunger shaft 43 is the chamber portion of composition between piston bush 37 and piston 42,
Hydraulic oil enters plunger shaft 43 by fuel feed hole 36, promotes piston 42 to overcome spring III 41 to promote valve 39 to open；Draining
The hole that hole 44 is opened by piston bush 37 upper left wall, its Main Function is to allow the hydraulic oil in plunger shaft 43 flow into fuel tank II 5, gas
Door 39 return under the effect of spring III 41.
As shown in Figure 10: the effect of electronics air relief valve 45 is the pressure of stabilisation systems, when lift control system pressure is higher than setting
During value, electronics air relief valve 45 draining can be passed through, make system pressure stable, pass through the pressure that electronics air relief valve 45 is different simultaneously
Setting value changes the lift of valve 39；Oil pipe III 46 sets up oil pipe road for device；Oil pipe I 47 sets up oil pipe road for device；
Fuel tank I 48 is common fuel tank, is used for storing hydraulic oil；Cleaner 49 is arranged between fuel tank I 48 and oil pump 50, its effect
For the hydraulic oil sucking oil pump 50 is filtered, it is ensured that the cleaning of hydraulic oil liquid；Oil pump 50 is common vane pump, for being
System provides the hydraulic oil of 2.5 8MPa, thus ensures the whole full variable valve lift control system demand for hydraulic oil；Oil
Pipe II 51 sets up oil pipe road for device.
Work process of the present utility model is divided into the three below stage:
1. valve 39 open stage, this stage cam I 2 drives plunger I G of valve opening and closing governor motion I A descending, cam
II 4 drive plunger II I of valve opening and closing governor motion II C up, the helicla flute of plunger I G in valve opening and closing governor motion I A
I 13 connect with oil duct I 24 and the oil duct II 18 of base B, the helicla flute II 32 of plunger II I in valve opening and closing governor motion II C
Connect with oil duct II 18 and the oil duct IV 21 of base B, and in valve opening and closing governor motion II C the helicla flute III 34 of plunger II I with
The oil duct III 23 of base B does not connects with oil duct V 22, hydraulic oil from fuel tank I 48 through cleaner 49 filter after by oil pump 50
Pump into electronics air relief valve 45, by flowing into oil pipe II 51 after electronics air relief valve 45 voltage stabilizing, then by oil duct I 24, helicla flute
I 13, oil duct II 18, helicla flute II 32, oil duct IV 21, fuel feed hole 36 flow into plunger shaft 43, when hydraulic oil is to hydraulic piston
When piston 42 pressure of valve group D be enough to overcome spring III 41 pretightning force and frictional force, valve 39 is promoted to open until arriving
High-lift.
2. valve 39 lift keeps the stage, and in valve opening and closing governor motion I A, the helicla flute I 13 of plunger I G is with base B's
Oil duct I 24 connects with oil duct II 18, the oil of the helicla flute II 32 and base B of plunger II I in valve opening and closing governor motion II C
Road II 18 connects with oil duct IV 21, and the oil of the helicla flute III 34 and base B of plunger II I in valve opening and closing governor motion II C
Road III 23 does not connects with oil duct V 22, and hydraulic oil supplies governor motion E, oil duct I 24, helicla flute I 13, oil at hydraulic oil
Forming path in road II 18, helicla flute II 32, oil duct IV 21, fuel feed hole 36, plunger shaft 43, electronics air relief valve 45 keeps this
In path, oil pressure is stablized constant, and valve 39 can be made to keep certain lift.
3. valve 39 falls the stage after rise, this stage convex when cam I 2 drive valve opening and closing governor motion I A plunger I G up,
The plunger II I of cam II 4 driving valve opening and closing governor motion II C is descending, the spiral shell of plunger I G in valve opening and closing governor motion I A
Spin slot I 13 does not connects with oil duct I 24 and the oil duct II 18 of base B, the spiral of plunger II I in valve opening and closing governor motion II C
Groove II 32 does not connects with oil duct II 18 and the oil duct IV 21 of base B, and hydraulic oil cannot subtract at cleaner 49, oil pump 50, electronics
Pressure valve 45, oil inlet pipe II 51, oil duct I 24, helicla flute I 13, helicla flute I 13, oil duct II 18, helicla flute II 32, oil duct
IV 21, fuel feed hole 36 and plunger shaft 43 form path, and the spiral of plunger II I in valve opening and closing governor motion II C simultaneously
Groove III 34 connects with oil duct III 23 and the oil duct V 22 of base B, make hydraulic oil in original plunger shaft 43 by oil leak hole 44,
Oil duct V 22, helicla flute III 34, oil duct III 23 flow into fuel tank II 5, complete the draining process of plunger shaft 43, and valve 39 is at bullet
Return under the effect of spring III 41.
Valve 39 timing and liter process control process:
Having helicla flute I 13 on plunger I G, regulation worm screw I 8 drives plunger I G to rotate by turbine axle sleeve I F, makes helicla flute
I 13 with the relative position changes of oil duct I 24 outlet, and then make the time changing that helicla flute I 13 connects with oil duct I 24, also
That is valve 39 start-up time can be changed by rotating screw groove I 13；Helicla flute III 34 is had, regulation on plunger II I
Worm screw II 27 drives plunger II I to rotate by turbine shaft sleeve II H, and the relative position making helicla flute III 34 export with oil duct V 22 changes
Become, and then the time changing that helicla flute III 34 connects with oil duct V 22, say, that can be changed by rotating screw groove III 34
Air valve variation 39 close moment；The effect of electronics air relief valve 45 is the pressure of stabilisation systems, by the pressure that electronics air relief valve 45 is different
Power setting value changes the lift of valve 39.The design mechanism, can make valve 39 lift and port timing equal by above method
Continuous variable, and this mechanism structure is simple, it is easy to control.
Claims (6)
1. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type, it is characterised in that: by valve opening and closing governor motion I (A),
Base (B), valve opening and closing governor motion II (C), hydraulic piston valve group (D), hydraulic oil supply governor motion (E), bolt I (1),
Cam I (2), bolt II (3), cam II (4) and fuel tank II (5) composition, the wherein plunger of valve opening and closing governor motion I (A)
I (G) top contacts with cam I (2)；The plunger I (G) of valve opening and closing governor motion I (A) is placed in the guide rail I (17) of base (B)
In, and the boss II (14) of plunger I (G) is slidably connected with guide rail I (17), the spring I (6) of valve opening and closing governor motion I (A)
Lower end is spacing by guide rail I (17) lower end；In valve opening and closing governor motion I (A), the location-plate I (7) of turbine axle sleeve I (F) is through bolt
I (1) is affixed with the bolt hole I (16) of base (B)；The spiral shell of plunger I (G) in valve opening and closing governor motion I (A) in induction stroke
Spin slot I (13) connects with oil duct I (24) and the oil duct II (18) of base (B)；The plunger II (I) of valve opening and closing governor motion II (C)
Top contacts with cam II (4)；The plunger II (I) of valve opening and closing governor motion II (C) is placed in the guide rail II (20) of base (B),
And boss IV (33) guide rail II (20) of plunger II (I) is slidably connected, spring II (25) lower end of valve opening and closing governor motion II (C)
Spacing by guide rail II (20) lower end；In valve opening and closing governor motion II (C), the location-plate II (26) of turbine shaft sleeve II (H) is through bolt
II (3) is affixed with the bolt hole II (19) of base (B)；Spiral shell in plunger II (I) in valve opening and closing governor motion II (C) in induction stroke
Spin slot II (32) connects with oil duct II (18) and the oil duct IV (21) of base (B)；Valve opening and closing governor motion II (C) in exhaust stroke
The helicla flute III (34) of middle plunger II (I) connects with the oil duct III (23) of base (B) and oil duct V (22)；Hydraulic piston valve group (D)
Fuel feed hole III (36) be connected with the oil duct IV (21) of base (B) through conduit；Oil leak hole III (44) warp of hydraulic piston valve group (D)
Conduit is connected with the oil duct V (22) of base (B)；The oil pipe II (51) of hydraulic oil supply governor motion (E) and the oil duct of base (B)
I (24) connection.
2. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type as described in claim 1, it is characterised in that: described gas
Door opening and closing governor motion I (A) is by turbine axle sleeve I (F), plunger I (G), spring I (6), location-plate I (7) and regulation worm screw
I (8) composition, wherein turbine axle sleeve I (F) is provided with chassis I (9), centre bore I (10) and turbine I (11)；Plunger I (G)
Top is provided with boss I (12), and plunger I (G) bottom is provided with boss II (14), and plunger I (G) bottom is provided with nose bar I (15)；Spiral shell
Spin slot I (13) is located at boss II (14) top；Spring I (6) is placed on the nose bar I (15) of plunger I (G)；Regulation worm screw I (8)
It is placed in turbine I (11) left end of turbine axle sleeve I (F)；Location-plate I (7) is pressed on the chassis I (9) of turbine axle sleeve I (F)；Turbine
The centre bore I (10) of axle sleeve I (F) is connected with boss I (12) spline gaps of plunger I (G).
3. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type as described in claim 1, it is characterised in that: the described end
Seat (B) left part is provided with guide rail I (17)；Base (B) right part is provided with plunger guide rail II (20)；The left portion of plunger guide rail I (17) is provided with
Oil duct I (24), and oil duct I (24) is opened on base (B) left surface；Plunger guide rail I (17) upper right quarter and guide rail II (20) upper left
The oil duct II (18) that portion is communicated with；Plunger guide rail II (20) lower left quarter is provided with oil duct III (23), and oil duct III (23) is opened on the end
Seat (B) bottom surface；Plunger guide rail II (20) upper right quarter is provided with oil duct IV (21), and oil duct IV (21) is opened on base (B) right flank；
Plunger guide rail II (20) right lower quadrant is provided with oil duct V (22), and oil duct V (22) is opened on base (B) right flank；The upper table of base (B)
Face is provided with bolt hole I (16) by plunger guide rail I (17) left side；Base (B) upper surface is provided with bolt by plunger guide rail II (20) left side
Hole II (19).
4. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type as described in claim 1, it is characterised in that: described gas
Door opening and closing governor motion II (C) is by turbine shaft sleeve II (H), plunger II (I), spring II (25), location-plate II (26) and regulation worm screw
II (27) composition, wherein turbine axle sleeve (H) is provided with chassis II (28), centre bore II (29) and turbine II (30)；Plunger II (I)
Top is provided with boss III (31), and plunger II (I) bottom is provided with boss IV (33), and plunger II (I) bottom is provided with nose bar II (35)；Spiral shell
Spin slot II (32) is located at boss IV (33) top, and helicla flute III (34) is located at boss IV (33) bottom；Spring II (25) is placed on plunger
The nose bar II (35) of II (I)；Regulation worm screw II (27) is placed in turbine II (30) left end of turbine shaft sleeve II (H)；Location-plate II (26)
It is pressed on the chassis II (28) of turbine shaft sleeve II (H)；The centre bore II (29) of turbine shaft sleeve II (H) and the boss III (31) of plunger II (I)
Spline gaps connects.
5. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type as described in claim 1, it is characterised in that: described liquid
Pressure piston port group (D) is made up of, wherein piston bush (37), valve (39), spring base (40), spring III (41) and piston (42)
Piston bush (37) upper left wall is provided with oil leak hole III (44), and piston bush (37) top is provided with fuel feed hole III (36)；Piston (42) is placed in work
In plug sleeve (37), and it is slidably connected with piston bush (37) inwall；Plunger shaft (43) is between piston (42) top and piston bush (37)
Chamber portion；Valve (39) bottom is connected with spring base (40), and valve (39) middle part is cased with spring III (41), valve (39)
Upper end is through the centre bore III (38) of piston bush (37) bottom, and affixed with piston (42) lower end, spring III (41) upper end is by piston
Set (37) bottom is spacing, and spring III (41) lower end is spacing by spring base (40).
6. the mechanic adjustment unit of the full changeable air valve of hydraulic drive type as described in claim 1, it is characterised in that: described liquid
Pressure oil feeder governor motion (E) by electronics air relief valve (45), oil pipe III (46), oil pipe I (47), fuel tank I (48), cleaner (49),
Oil pump (50) and oil pipe II (51) composition, oil pump (50) lower end is connected with cleaner (49) upper end, oil pump (50) upper end and oil pipe
II (51) lower end connects, and cleaner (49) lower end is connected with fuel tank I (48), and oil pipe I (47) entrance is placed in fuel tank I (48),
Oil pipe I (47) outlet is connected with cleaner (49) upper end；Oil pipe III (46) middle part is provided with electronics air relief valve (45), oil pipe III (46)
Left end connects with oil pipe II (51), and oil pipe III (46) outlet is placed in fuel tank I (48).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620348185.XU CN205578058U (en) | 2016-04-23 | 2016-04-23 | Full variable valve's of hydraulic drive formula mechanical regulating unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620348185.XU CN205578058U (en) | 2016-04-23 | 2016-04-23 | Full variable valve's of hydraulic drive formula mechanical regulating unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205578058U true CN205578058U (en) | 2016-09-14 |
Family
ID=56859958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620348185.XU Withdrawn - After Issue CN205578058U (en) | 2016-04-23 | 2016-04-23 | Full variable valve's of hydraulic drive formula mechanical regulating unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205578058U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105781656A (en) * | 2016-04-23 | 2016-07-20 | 吉林大学 | Mechanical adjusting device of hydraulic drive type fully-variable valve |
| CN107676142A (en) * | 2017-11-13 | 2018-02-09 | 吉林大学 | A kind of hydraulic-driven variable valve actuator for air of low voltage control high pressure |
| CN109715911A (en) * | 2016-09-29 | 2019-05-03 | 舍弗勒技术股份两合公司 | The internal combustion engine of ventilation valve transmission device with hydraulic variable |
-
2016
- 2016-04-23 CN CN201620348185.XU patent/CN205578058U/en not_active Withdrawn - After Issue
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105781656A (en) * | 2016-04-23 | 2016-07-20 | 吉林大学 | Mechanical adjusting device of hydraulic drive type fully-variable valve |
| CN105781656B (en) * | 2016-04-23 | 2017-12-01 | 吉林大学 | A kind of mechanic adjustment unit of the full changeable air valve of hydraulic drive type |
| CN109715911A (en) * | 2016-09-29 | 2019-05-03 | 舍弗勒技术股份两合公司 | The internal combustion engine of ventilation valve transmission device with hydraulic variable |
| US10900389B2 (en) | 2016-09-29 | 2021-01-26 | Schaeffler Technologies AG & Co. KG | Internal combustion engine with a hydraulically variable gas exchange valve train |
| CN109715911B (en) * | 2016-09-29 | 2021-10-12 | 舍弗勒技术股份两合公司 | Internal combustion engine with hydraulically variable gas exchange valve gear |
| CN107676142A (en) * | 2017-11-13 | 2018-02-09 | 吉林大学 | A kind of hydraulic-driven variable valve actuator for air of low voltage control high pressure |
| CN107676142B (en) * | 2017-11-13 | 2023-09-29 | 吉林大学 | Hydraulic drive variable valve mechanism with low pressure control and high pressure |
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