CN104564206A - Cam-driven hydraulic fully variably valve mechanism of internal combustion engine - Google Patents
Cam-driven hydraulic fully variably valve mechanism of internal combustion engine Download PDFInfo
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- CN104564206A CN104564206A CN201510035476.3A CN201510035476A CN104564206A CN 104564206 A CN104564206 A CN 104564206A CN 201510035476 A CN201510035476 A CN 201510035476A CN 104564206 A CN104564206 A CN 104564206A
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- valve
- piston
- tappet
- oil
- oil pipe
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Classifications
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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
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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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
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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
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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
Abstract
A cam-driven hydraulic fully variable valve mechanism of an internal combustion engine belongs to the technical field of engines. An inlet end of an oil tube III is arranged in an oil tank I, an outlet end of the oil tube is fixedly connected with an oil inlet hole I. The inlet end of the oil tube III is provided with a filter. An oil pump, an inlet end of an oil tube II and a check valve I are connected with the oil tube III in series. An overflow valve and an outlet end of an oil tube I are connected with the oil tube II in series. An outlet end of the oil tube II is arranged in the oil tank I. An inlet end of the oil tube I is fixedly connected with an oil drainage hole. The middle of the oil tube I is provided with a check valve II. The inlet end of an oil tube V is fixedly connected with an oil drainage hole II. The outlet end of the oil tube V is arranged in the oil tank II. An electro-hydraulic proportional valve is arranged adjacent to the inlet end of the oil tube V. The two ends of an oil tube IV are respectively communicated with a connecting hole and an oil inlet hole II of a tappet group. A check valve II is arranged in the middle of the oil tube IV. The cam-driven hydraulic fully variable valve mechanism of the internal combustion engine can realize continuous variable of valve lift and valve timing and throttle-free load control of a gasoline engine, reduce pumping loss, improve the volumetric efficiency, realize the Miller cycle, achieves the effect of energy saving and emission reduction, and is simple in structure and flexible in control.
Description
Technical field
The invention belongs to technical field of engines, be specifically related to a kind of actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air.
Background technique
The distribution device of conventional engines, because structure is fixed, in engine operation process, port timing is unalterable, usually can only ensure the performance at a certain operation optimization internal-combustion engine, the requirement of each operating mode can not be taken into account simultaneously, be difficult to reach real best port timing.These fixing valve Operational Limitss are that internal-combustion engine runs the one of the various comprehensive contradiction of valve job requirement compromise under different operating mode.Therefore, in order to port timing demand different under satisfied different operating mode, improve internal-combustion engine Economy and power character, reduce hazardous emission, need to adopt changeable air valve technology.Changeable air valve technology can according to the change of engine conditions, realizes the continuous variable of valve lift from zero to design maximum lift and port timing.
Because changeable air valve technology has huge superiority, it has become a focus direction of Current internal combustion engines research, and some institution of higher learning and scientific research institution expand the research work to variable valve actuator for air in succession both at home and abroad.Although at present variable valve actuator for air is of a great variety, working principle is also not quite similar, and according to the difference of its structural feature and driving mode, variable valve actuator for air can be divided into substantially cam drive mechanism and without the large class of cam drive mechanism two.Wherein can realize the flexible control to valve lift and port timing without actuated by cams variable valve actuator for air, but relate to multiple fields such as hydraulic pressure, electromagnetism, electronics due to it, complex structure and larger volume need be taken; And cam-actuated variable valve actuator for air, mechanism is relatively simple and reliable, but due to the narrow limitation of original cam mechanism, often can not control valve lift and port timing flexibly.
Summary of the invention
The object of the invention is to overcome existing variable valve actuator for air complex structure, volume is larger, and the shortcoming such as valve lift and port timing can not be controlled flexibly, there is provided a kind of simple and reliable for structure, and the actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air of valve lift and port timing can be controlled flexibly.
The present invention forms by by hydraulic piston valve group A, tappet group B, cam 1, oil pipe I 2, fuel tank I 3, filter cleaner 4, oil pipe II 5, oil pump 6, relief valve 7, oil pipe III 8, one-way valve I 9, one-way valve II 10, one-way valve III 11, oil pipe IV 12, electro-hydraulic proportional valve 13, oil pipe V 14 and fuel tank II 15, wherein oil pipe III 8 entry end is placed in fuel tank I 3, and the tappet that oil pipe III 8 outlet end is fixed in tappet group B overlaps the oil inlet hole I 29 at 33 tops; Oil pipe III 8 entry end is equipped with filter cleaner 4, is serially connected with oil pump 6, oil pipe II 5 entry end and one-way valve I 9 between oil pipe III 8 entry end and oil pipe III 8 outlet end; Be serially connected with relief valve 7 and oil pipe I 2 outlet end between oil pipe II 5 entry end and oil pipe II 5 outlet end, oil pipe II 5 outlet end is placed in fuel tank I 3; The oil leak hole I 27 of oil pipe I 2 entry end and tappet group (B) is affixed, is equipped with one-way valve II 10 in the middle part of oil pipe I 2; Oil pipe V 14 entry end is fixed in the oil leak hole II 22 of hydraulic piston valve group A, and oil pipe V 14 outlet end is placed in fuel tank II 15, and the nearly entry end of oil pipe V 14 is equipped with electro-hydraulic proportional valve 13; Oil pipe IV 12 entry end is fixed in the attachment hole 32 of tappet group B, and oil pipe IV 12 outlet end is communicated with the oil inlet hole II 21 of hydraulic piston valve group A, is equipped with one-way valve III 11 in the middle part of oil pipe IV 12.
Described hydraulic piston valve group A is made up of valve 16, cotter seat I 17, valve spring I 18, valve piston 19, piston cavity 20 and piston sleeve 23, wherein piston sleeve 23 top is provided with oil inlet hole II 21, piston sleeve 23 upper right wall is provided with oil leak hole II 22, valve piston 19 is placed in piston sleeve 23, be slidably connected with piston sleeve 23 inwall, piston cavity 20 is the chamber portion between valve piston 19 top and piston sleeve 23, and for valve piston 19 piston sleeve 23 inwall slide leading role is provided; Valve 16 is connected with cotter seat I 17, cover has valve spring I 18 again, valve 16 upper end is affixed through the center hole bottom piston sleeve 23 and valve piston 19 lower end, and valve spring I 18 upper and lower end is respectively by spacing with cotter seat I 17 bottom piston sleeve 23.
Described tappet group B is made up of joint tongue 24, fuel-flow control sleeve 25, gear ring clamping screw 26, tappet chamber 28, spiral chute 30, tappet piston 31, tappet cover 33, fuel-flow control ratch sleeve 34, fuel-flow control ratch 35, gear ring 36, joint tongue groove 37, piston rod 38, spring II 39, spring seat II 40, wherein tappet overlaps 33 tops and is provided with oil inlet hole I 29, tappet overlaps 33 left side central portion and is provided with oil leak hole I 27, and tappet overlaps 33 right upper portion and is provided with attachment hole 32; Tappet piston 31 is positioned at tappet cover 33, and tappet piston 31 top and tappet overlap 33 inwalls and be slidably connected; Tappet chamber 28 is the chamber portion that tappet piston 31 top and tappet overlap between 33, and provides guiding for tappet piston 31 overlaps 33 inwalls slips at tappet, and tappet piston 31 is provided with spiral chute 30; It is affixed that the tappet of fuel-flow control sleeve 25 top inner ring and oil leak hole less than I 27 overlaps 33 outer rings; Fuel-flow control sleeve 25 bottom inner ring and joint tongue groove 37 outer ring affixed; Piston rod 38 top of tappet piston 31 through the hole at joint tongue groove 37 top and tappet piston 31 affixed; Affixed with joint tongue 24 in the middle part of the piston rod 38 of tappet piston 31, joint tongue 24 and joint tongue groove 37 are slidably connected, and piston rod 38 lower end and the spring seat II 40 of tappet piston 31 are affixed; Spring II 39 is placed on piston rod 38 bottom of tappet piston 31, the upper and lower end of spring II 39 respectively by fuel-flow control sleeve 25 lower end and spring seat II 40 spacing; Gear ring 36 is fixed in side, top, fuel-flow control sleeve 25 outer ring through gear ring clamping screw 26, and fuel-flow control ratch 35 engages with gear ring 36, and fuel-flow control ratch 35 is fixed in fuel-flow control ratch sleeve 34; Spring seat II 40 lower end contacts with cam 1.
Cam 1 contacts with tappet piston 31 lower end spring seat II 40 further, valve 16 is connected with cotter seat I 17, cover has valve spring I 18 again, valve 16 upper end through the center hole bottom piston sleeve 23 and valve piston 19 lower end affixed, valve spring I 18 upper and lower end is respectively by spacing with cotter seat I 17 bottom piston sleeve 23, cam 1 drives tappet piston 31 up, and the oil pressure in high-pressure system rises, and promotion valve piston 19 overcomes valve spring I 18 promotion valve 16 and opens.Filter cleaner 4 lower end is connected with fuel tank I3, upper end is connected with oil pump 6 lower end, oil pump 6 upper end connects a three-way union, this three-way union lower end connects oil pump 6 upper end, right-hand member connects relief valve 7 left end, upper end connects one-way valve I9 left end, and the tappet of one-way valve I9 right-hand member connection tappet group B overlaps the oil inlet hole I 29 at 33 tops.One-way valve II10 left end connects a three-way union, and this three-way union upper end connects relief valve 7 right-hand member, and left end connects one-way valve II9 right-hand member, and lower end connects fuel tank I2, and one-way valve II9 connects the oil leak hole I 27 of tappet group (B).One-way valve III11 left end connects the attachment hole 32 of tappet group B, and right-hand member connects and is communicated with the oil inlet hole II 21 of hydraulic piston valve group A, and electro-hydraulic proportional valve 13 left end connects the oil leak hole II22 on hydraulic pressure piston port group A piston sleeve 19, and right-hand member connects fuel tank II15.
The present invention can be divided into low service system and high-pressure system according to hydraulic system, low service system comprises fuel tank I3, filter cleaner 4, oil pump 6, relief valve 7, one-way valve I9, fuel tank II15, high-pressure system comprises tappet chamber 28, tappet piston 31, tappet cover 33, one-way valve III11, valve piston 19, piston cavity 20 and piston sleeve 23, and tappet cover 33 has oil inlet hole I 29, oil leak hole I27 and attachment hole 32, piston sleeve 23 has oil inlet hole II21 and oil leak hole II 22.First oil inlet hole I 29, oil leak hole I27, oil leak hole II 22 are all closed, cam 1 drives the tappet piston 31 of tappet group B up, oil pressure in high-pressure system rises, the valve piston 19 promoting hydraulic piston valve group A overcomes valve spring I 18 promotion valve 16 and opens, when valve 16 arrives appointment lift, one-way valve III11 can keep valve lift.Open electro-hydraulic proportional valve 13, high pressure oil is flowed out by oil leak hole II22, valve 16 return under the effect of valve spring I 18.When cam 1 is in descending branch, tappet piston 31 starts to fall after rise, and now valve 16 is in and takes a seat or taking a seat in process, when valve 16 and tappet piston 31 are all taken a seat, completes once complete valve 16 opening-closing process.
In conjunction with each assembly of the present invention and mounting point relation thereof, actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air of the present invention is achieved through the following technical solutions:
1. when motor is in low speed Smaller load, induction air flow ratio is low, and fluid inertial flow is little, should adopt less valve 16 lift, is conducive to strengthening In Cylinder Flow, improves velocity of combustion, increases low engine speed moment of torsion, improves cold start-up and reduces oil consumption.As shown in Figure 3, see the spiral chute 30 that turns clockwise from top to bottom, spiral chute 30 can be made to close moment of oil leak hole I 27 delayed, make valve 16 open evening simultaneously and diminish with valve 16 lift; Now coordinate the start-up time of electro-hydraulic proportional valve 13 to realize the control of IO Intake Valve Opens endurance and also can realize petrol engine non-air throttle spatial load forecasting and miller cycle.
2. when motor be at a high speed large load time, induction air flow ratio is high, fluid inertial flow is large, larger valve lift should be adopted, open intake valve ahead of time, reduce valve throttling loss, improve charging efficiency, improve the power stage of motor when the large load of high speed, and reduce fuel consume, improve fuel economy.As shown in Figure 3, see from top to bottom and be rotated counterclockwise spiral chute 30, valve 16 can be made early to open, and valve 16 lift becomes large.
3. tappet piston 31 angle of swing is certain, then the lift of valve 16 and start-up time certain, after valve 16 arrives maximum lift, descending along with tappet piston 31, in tappet chamber 28, hydraulic fluid pressure declines, one-way valve III11 closes immediately due to the effect of pressure reduction, valve 16 lift remains on maximum position, and now controlled the start-up time of electro-hydraulic proportional valve 13 by ECU and engine control computer, piston cavity 29 internal pressure declines, valve 16 is up, can realize the control of IC Intake Valve Closes moment; Take a seat the later stage, reduce the circulation area of electro-hydraulic proportional valve 13, thus control the seating velocity of valve 16, realize soft taking a seat.
Beneficial effect of the present invention is:
1. can realize the continuous variable of valve lift, port timing, and valve maximum lift can be kept within a certain period of time.
2. structure is simple, controls flexibly.
3. can realize petrol engine non-air throttle spatial load forecasting, reduce pumping loss, improve charging efficiency and realize miller cycle, reaching the effect of energy-saving and emission-reduction.
Accompanying drawing explanation
Fig. 1 is the structural representation of actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air
Fig. 2 is the structural representation of hydraulic piston valve group
Fig. 3 is the structural representation of tappet group
Fig. 4 is the sectional structure schematic diagram in C-C direction in Fig. 2
Fig. 5 is the sectional structure schematic diagram in D-D direction in Fig. 2
Including: a. hydraulic piston valve group b. lifter group 1. 2. CAM tubing Ⅰ 3. 4 tank Ⅰ filter 5. Tubing Ⅱ 6. Oil pump 7. 8. The overflow valve tubing Ⅲ 9. One-way valve Ⅰ 10. Check valve Ⅱ 11. A one-way valve Ⅲ 12. Tubing Ⅳ 13. Electro-hydraulic proportional valve 14. Tubing Ⅴ 15. Tank Ⅱ 16. Valve 17. Ⅰ 18. The valve spring seat valve springs Ⅰ 19. The valve piston, piston chamber 21. The oil hole Ⅱ 22. The drainage hole Ⅱ 23. The piston set of 24. The tenon 25. The fuel control sleeve 26. The gear ring clamp screw 27 drainage hole Ⅰ 28. A cylindrical cavity 29 oil hole Ⅰ 30. Spiral groove 31 lifter piston 32. Connecting hole 33. Lifter set of 34 fuel control gear rod sleeve 35 fuel control gear lever 36 ring gear with A tenon chamfer 38. 39. The piston rod spring Ⅱ 40. The spring seat Ⅱ
Embodiment
Below in conjunction with accompanying drawing, the present invention is described in detail:
The present invention is by by hydraulic piston valve group A, tappet group B, cam 1, oil pipe I 2, fuel tank I 3, filter cleaner 4, oil pipe II 5, oil pump 6, relief valve 7, oil pipe III 8, one-way valve I 9, one-way valve II 10, one-way valve III 11, oil pipe IV 12, electro-hydraulic proportional valve 13, oil pipe V 14 and fuel tank II 15 form, described hydraulic piston valve group A is by valve 16, cotter seat I 17, valve spring I 18, valve piston 19, piston cavity 20 and piston sleeve 23 form, described tappet group B is by joint tongue 24, fuel-flow control sleeve 25, gear ring clamping screw 26, tappet chamber 28, spiral chute 30, tappet piston 31, tappet cover 33, fuel-flow control ratch sleeve 34, fuel-flow control ratch 35, gear ring 36, joint tongue groove 37, piston rod 38, spring II 39, spring seat II 40 forms.
With reference to accompanying drawing 1:
Cam 1 is mainly whole variable valve actuator for air and provides power, drives valve 16 to open and close.
Fuel tank I3 and fuel tank II15 is common fuel tank, for storage liquid force feed.
Filter cleaner 4 is arranged between fuel tank I3 and oil pump 6, and its hydraulic oil act as sucking oil pump 6 filters, and ensures the clean of hydraulic oil liquid.
Oil pump 6 is common gear pump, for system provides the hydraulic oil of 0.2-0.5MPa, thus ensure the demand of whole full variable valve system for hydraulic oil, when cam 1 is in descending branch, tappet 31 starts to fall after rise, the situation that fluid pressure in high-pressure system will there will be higher or lower than low service system pressure, when hydraulic coupling is closed higher than one-way valve I9 during low service system pressure, when hydraulic coupling is lower than low service system pressure, one-way valve I9 opens, and the hydraulic oil in low service system enters high-pressure system by one-way valve I9 and oil inlet hole I 29.
The effect of relief valve 7 is the pressure of stabilizing low voltage system, when low service system pressure is higher than setting value, can pass through relief valve 7 draining, and system pressure is stablized.
The Main Function of one-way valve I9 is separated with low service system high-pressure system, can be the timely repairing of high-pressure system, also can prevent the hydraulic oil in high-pressure system from entering low service system.
The Main Function of one-way valve III11 makes valve 16 lift keep the regular hour, and the high pressure oil in piston cavity 20 can not be flow backwards into tappet chamber 28.
The Main Function of electro-hydraulic proportional valve 13 is that hydraulic oil is flowed out by certain flow and speed, ensures that valve 16 is steadily taken a seat, and can realize the control of IC Intake Valve Closes moment.
With reference to accompanying drawing 2:
Valve spring I 18 upper and lower end is respectively by spacing with cotter seat I 17 bottom piston sleeve 23.
The Main Function of valve spring I 18 ensures that valve 16 is taken a seat in time, and maintain between each part of mechanism normal contact, secondly, valve spring I 18 also has the pressure that increases valve 16 pairs of cotter seats I 17 and improves the effect that valve 16 seals.
Valve piston 19 lower end and valve 16 affixed, the Main Function of valve piston 19 overcomes valve spring I 18 active force, and promote valve 16 and open.
Piston cavity 20 is the chamber portion formed between piston sleeve 23 and valve piston 19, and the high pressure oil in tappet chamber 28 enters piston cavity 20 by one-way valve III11, and promotion valve piston 19 overcomes valve spring I 18 promotion valve 16 and opens.
The hole that oil inlet hole II 21 is opened for piston sleeve 23 top, its Main Function provides passage for the high pressure oil in tappet chamber 28 enters piston cavity 20.
The hole that oil leak hole II 22 is opened for piston sleeve 23 upper right wall, its Main Function allows the high pressure oil in piston cavity 20 flow into fuel tank II15, open electro-hydraulic proportional valve 13, high pressure oil flows into fuel tank II13 by oil leak hole II22, valve 16 return under the effect of valve spring I 18.
Piston sleeve 23 can be valve piston 19 motion and provides guiding, piston sleeve 23 has oil inlet hole II21 and oil leak hole II 22.
With reference to accompanying drawing 3:
Affixed in the middle part of the piston rod 38 of joint tongue 24 and tappet piston 31, the piston rod 38 of joint tongue 24 and tappet piston 31 can slide in joint tongue groove 37, when fuel-flow control ratch 35 pulls fuel-flow control sleeve 25 to rotate, fuel-flow control sleeve 25 drives the piston rod 38 of joint tongue 24 and tappet piston 31 to rotate by joint tongue groove 37, thus tappet piston 31 is rotated.
It is affixed that the tappet of fuel-flow control sleeve 25 top inner ring and oil leak hole less than I 27 overlaps 33 outer rings, fuel-flow control sleeve 25 bottom inner ring and joint tongue groove 37 outer ring affixed, joint tongue groove 37 and joint tongue 24 are slidably connected, tappet piston 31 can be made to rotate by fuel-flow control sleeve 25, thus change valve 16 lift and air inlet timing.
The Main Function of gear ring clamping screw 26 is that gear ring 36 is clamped on fuel-flow control sleeve 25, occurs loosening when preventing fuel-flow control ratch 35 from pulling tappet piston 31 to rotate.
The hole of oil leak hole I27 for tappet cover 33 is opened, its Main Function allows the hydraulic oil of high-pressure system in time flow into fuel tank I3, makes system not set up high pressure, thus can not open valve 16.
Tappet chamber 28 is the chamber portion of composition between tappet cover 33 and tappet piston 31, its Main Function stores the hydraulic oil flowed into by low service system, tappet piston 31 is by the hydraulic oil in compression tappet chamber 28, make intrasystem oil pressure increase, promotion valve piston 19 overcomes valve spring I 18 promotion valve 16 and opens.
The hole of oil inlet hole I 29 for tappet cover 33 is opened, its Main Function is that the hydraulic oil for being entered high-pressure system by low service system provides passage.
Spiral chute 30 is opened on tappet piston 31, can change valve 16 lift and port timing by the relative position changing spiral chute 30 and oil leak hole I27, and structure is simple, and it is convenient to control.
The piston rod 38 of tappet piston 31 is contacted with cam 1 by spring seat II 40, and the Main Function of tappet piston 31 is the hydraulic oil in compression tappet chamber 28, and oil pressure is raised.In addition, tappet piston 31 has spiral chute 30, the fuel-flow control ratch 35 of oil amount regulating mechanism pulls tappet piston 31 to rotate, when spiral chute 30 is connected with oil leak hole I27, high pressure oil can not be set up in high-pressure system, also just can not promote piston 19 overcome valve spring I 18 promote valve 16 open, that is can change valve 16 lift and start-up time by rotating screw groove 30.
The hole of attachment hole 32 for tappet cover 33 is opened, attachment hole 32 and oil inlet hole II 21 are connected tappet chamber 28 and piston cavity 20 together, provide passage for the high pressure oil in tappet chamber 28 enters piston cavity 20.
It is for tappet piston 31 motion provides guiding that tappet overlaps 33 Main Functions, and it has oil inlet hole I 29, oil leak hole I27 and attachment hole 32, hydraulic oil can be made in time to flow into or flow out high-pressure system and make the high pressure oil in tappet chamber 28 enter piston cavity 20.
Fuel-flow control ratch 35 goes to engage with gear ring 36, and by gear ring 36, tappet piston 31 is rotated, and the time changing unlatching oil leak hole I27 changes valve 16 lift and air inlet timing.
Gear ring 36 is fixed in side, top, fuel-flow control sleeve 25 outer ring through gear ring clamping screw 26, it is meshed with fuel-flow control ratch 35, fuel-flow control ratch 35 pulls tappet piston 31 to rotate, when spiral chute 30 is connected with oil leak hole I27, can not high pressure oil be set up in high-pressure system, also just can not promote piston 19 overcome valve spring I 18 promote valve 16 open.
Joint tongue groove 37 outer ring is affixed with fuel-flow control sleeve 25 bottom inner ring, and provides guiding for joint tongue 24 slides.The rotation of joint tongue groove 37 can drive the piston rod 38 of joint tongue 24 and tappet piston 31 to rotate, thus tappet piston 31 is rotated.
Piston rod 38 top is affixed through hole and the tappet piston 31 at joint tongue groove 37 top, lower end and spring seat II 40 affixed, its Main Function is the motion of transmission cam 1, and column piston 31 can be made to rotate.
Spring II 39 upper and lower end respectively by fuel-flow control sleeve 25 lower end and spring seat II 40 spacing, the effect of spring II 39 is that when ensureing that cam 1 declines, spring seat II 40 contacts with cam 1 all the time.
Spring seat II 40 lower end contacts with cam 1, and by the Movement transmit of cam 1 to piston rod 38, and by piston rod 38 by the Movement transmit of cam 1 to tappet piston 31, make it compress hydraulic oil in tappet chamber 28, oil pressure raised.
Working procedure of the present invention is divided into following four-stage:
1. valve 16 open stage, this stage oil inlet hole I 29, oil leak hole I27, oil leak hole II 22 are all closed, cam 1 drives tappet piston 31 up by spring seat II 40, oil pressure in high-pressure system rises, when oil pressure is enough to overcome valve spring I 18 pretightening force and frictional force, valve 16 is opened, until arrive maximum lift.
2. valve 16 lift keeps the stage, and this stage, one-way valve III11 closed, and the high pressure oil in piston cavity 20 does not flow backwards by one-way valve III11, and this stage valve 16 by the control of cam 1 molded line, can not make the lift that valve 16 keeps certain.
3. valve 16 falls the stage after rise, and this stage electro-hydraulic proportional valve 13 is opened, and the high pressure oil in piston cavity 20 is flowed out by oil leak hole II22, valve 16 return under the effect of valve spring I 18, and this stage valve 16 is not also by the control of cam 1 molded line.The working principle of electro-hydraulic proportional valve 13 is that in valve, proportion electro-magnet produces corresponding actions according to the voltage signal of input, makes operating valve spool produce displacement, port size change and complete the pressure proportional with input voltage with this, flow exports.Can be controlled electro-hydraulic proportional valve 13 by corresponding ECU (Electrical Control Unit), the high pressure oil in piston cavity 20 be flowed out by certain flow, and then valve 16 close moment and seating velocity can be controlled.
4. tappet falls the stage after rise, when cam 1 is in descending branch, tappet piston 31 starts to fall after rise, the situation that fluid pressure in high-pressure system will there will be higher or lower than low service system pressure, when hydraulic coupling is closed higher than one-way valve I9 during low service system pressure, when hydraulic coupling is lower than low service system pressure, one-way valve I9 opens, and the hydraulic oil in low service system enters high-pressure system by one-way valve I9 and oil inlet hole I 29.So far, complete a complete working procedure, and be that subsequent work process is ready.
Valve 16 timing and lift control procedure:
Tappet piston 31 has spiral chute 30, the fuel-flow control ratch 35 of oil amount regulating mechanism pulls tappet piston 31 to rotate, when spiral chute 30 does not close oil leak hole I27, hydraulic oil in high-pressure system flows back to fuel tank I3 by oil leak hole I27 and one-way valve II10, therefore high pressure can not be set up in high-pressure system, also just can not promoting piston 19 to overcome valve spring I 18 and promote valve 16 and open, that is can change valve 16 lift and start-up time by changing the angle of swing of spiral chute 30.As shown in Figure 3, see the spiral chute 30 that turns clockwise from top to bottom, valve 16 can be made to open evening, electro-hydraulic proportional valve 13 can flow out by certain flow and flow velocity by the high pressure oil in control piston chamber 20, thus the close moment of valve 16 can be controlled, realize the soft of valve 16 and take a seat.Tappet piston 31 coordinates electro-hydraulic proportional valve 13 conbined usage, can make valve 16 lift and the equal continuous variable of port timing, and this mechanism structure is simple, is easy to control.
Claims (3)
1. an actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air, by hydraulic piston valve group (A), tappet group (B), cam (1), oil pipe I (2), fuel tank I (3), filter cleaner (4), oil pipe II (5), oil pump (6), relief valve (7), oil pipe III (8), one-way valve I (9), one-way valve II (10), one-way valve III (11), oil pipe IV (12), electro-hydraulic proportional valve (13), oil pipe V (14) and fuel tank II (15) form, it is characterized in that wherein oil pipe III (8) entry end is placed in fuel tank I (3), oil pipe III (8) outlet end is fixed in the oil inlet hole I (29) at tappet cover (33) top of tappet group (B), oil pipe III (8) entry end is equipped with filter cleaner (4), is serially connected with oil pump (6), oil pipe II (5) entry end and one-way valve I (9) between oil pipe III (8) entry end and oil pipe III (8) outlet end, be serially connected with relief valve (7) and oil pipe I (2) outlet end between oil pipe II (5) entry end and oil pipe II (5) outlet end, oil pipe II (5) outlet end is placed in fuel tank I (3), the oil leak hole I (27) of oil pipe I (2) entry end and tappet group (B) is affixed, and oil pipe I (2) middle part is equipped with one-way valve II (10), oil pipe V (14) entry end is fixed in the oil leak hole II (22) of hydraulic piston valve group (A), oil pipe V (14) outlet end is placed in fuel tank II (15), and the nearly entry end of oil pipe V (14) is equipped with electro-hydraulic proportional valve (13), oil pipe IV (12) entry end is fixed in the attachment hole (32) of tappet group (B), oil pipe IV (12) outlet end is communicated with the oil inlet hole II (21) of hydraulic piston valve group (A), and oil pipe IV (12) middle part is equipped with one-way valve III (11).
2. by actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air according to claim 1, it is characterized in that described hydraulic piston valve group (A) is by valve (16), cotter seat I (17), valve spring I (18), valve piston (19), piston cavity (20) and piston sleeve (23) composition, wherein piston sleeve (23) top is provided with oil inlet hole II (21), piston sleeve (23) upper right wall is provided with oil leak hole II (22), valve piston (19) is placed in piston sleeve (23), be slidably connected with piston sleeve (23) inwall, piston cavity (20) is the chamber portion between valve piston (19) top and piston sleeve (23), valve (16) is connected with cotter seat I (17), cover has valve spring I (18) again, valve (16) upper end is affixed through center hole and valve piston (19) lower end of piston sleeve (23) bottom, valve spring I (18) upper and lower end respectively by bottom piston sleeve (23) and cotter seat I (17) spacing.
3. by actuated by cams formula internal-combustion engine hydraulic pressure fully variable valve actuator for air according to claim 1, it is characterized in that described tappet group (B) is by joint tongue (24), fuel-flow control sleeve (25), gear ring clamping screw (26), tappet chamber (28), spiral chute (30), tappet piston (31), tappet cover (33), fuel-flow control ratch sleeve (34), fuel-flow control ratch (35), gear ring (36), joint tongue groove (37), piston rod (38), spring II (39), spring seat II (40) forms, wherein tappet cover (33) top is provided with oil inlet hole I (29), tappet cover (33) left side central portion is provided with oil leak hole I (27), tappet cover (33) right upper portion is provided with attachment hole (32), tappet piston (31) is positioned at tappet cover (33), tappet piston (31) top and tappet cover (33) inwall are slidably connected, tappet chamber (28) is provided with spiral chute (30) for the chamber portion between tappet piston (31) top and tappet cover (33), tappet piston (31), fuel-flow control sleeve (25) top inner ring and oil leak hole I (27) tappet cover (33) outer ring is below affixed, fuel-flow control sleeve (25) bottom inner ring and joint tongue groove (37) outer ring affixed, piston rod (38) top of tappet piston (31) through the hole at joint tongue groove (37) top and tappet piston (31) affixed, piston rod (38) middle part of tappet piston (31) is affixed with joint tongue (24), joint tongue (24) and joint tongue groove (37) are slidably connected, piston rod (38) lower end and the spring seat II (40) of tappet piston (31) are affixed, spring II (39) is placed on piston rod (38) bottom of tappet piston (31), the upper and lower end of spring II (39) respectively by fuel-flow control sleeve (25) lower end and spring seat II (40) spacing, gear ring (36) is fixed in side, fuel-flow control sleeve (25) top, outer ring through gear ring clamping screw (26), fuel-flow control ratch (35) engages with gear ring (36), and fuel-flow control ratch (35) is fixed in fuel-flow control ratch sleeve (34), spring seat II (40) lower end contacts with cam (1).
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| CN201510035476.3A CN104564206A (en) | 2015-01-23 | 2015-01-23 | Cam-driven hydraulic fully variably valve mechanism of internal combustion engine |
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| CN201510035476.3A CN104564206A (en) | 2015-01-23 | 2015-01-23 | Cam-driven hydraulic fully variably valve mechanism of internal combustion engine |
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