CN205400837U - Cam drive type engine hydraulic pressure gas door control device - Google Patents
Cam drive type engine hydraulic pressure gas door control device Download PDFInfo
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- CN205400837U CN205400837U CN201620173009.7U CN201620173009U CN205400837U CN 205400837 U CN205400837 U CN 205400837U CN 201620173009 U CN201620173009 U CN 201620173009U CN 205400837 U CN205400837 U CN 205400837U
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Abstract
The utility model belongs to the technical field of the engine, concretely relates to cam drive type engine hydraulic pressure gas door control device, overcome the shortcoming that valve mechanism that prior art exists can not change valve lift and open the duration, solved when the valve is taken a seat the impact problem to valve seat insert, it takes a seat buffer gear, valve lift control mechanism, check valve I, oil pump and oil tank I, valve lift control mechanism and includes check valve II and cam I to open duration control mechanism and valve including hydraulic piston valve group, valve, oil tank I communicates with each other with check valve I, check valve II respectively, the oil pump sets up at check valve I and oil tank between I, hydraulic piston valve component do not communicate with each other with check valve I, check valve II, hydraulic piston valve group and valve are opened duration control mechanism and valve and are taken a seat buffer gear and communicate with each other through oil pipe I, oil pipe II. The utility model discloses simple structure, change valve lift that can be nimble with open the duration.
Description
Technical field
This utility model belongs to technical field of engines, is specifically related to a kind of actuated by cams formula hydraulic engine valve and controls device.
Background technology
In the valve actuating mechanism of conventional engines, the unlatching of valve is by actuated by cams, and therefore the lift of valve and the unlatching duration of valve are immutable.But in electromotor real work, need bigger valve stroke when big load and open the duration, and valve stroke is reduced during Smaller load, opening time reduction etc.；So the compromise of the various integration requirements under different operating modes, valve operation required is taked in the design of valve actuating mechanism.Therefore to meet the demand of different operating mode and the application of other Technolqgy for Energy Economizings, improve internal combustion engine economy and dynamic property, reduce hazardous emission, it is necessary to adopt lift range variable and the technology of variable unlatching duration.Simultaneously for hydraulic drive mechanism, owing to eliminating the camshaft direct control to valve, very easily cause and produce to impact to valve retainer during air valve drop, valve parts are caused damage.Therefore, process of hydraulic engine valve mechanism being taken a seat also should control effectively.
Summary of the invention
Technical problem to be solved in the utility model is to overcome the valve mechanism that prior art exists to change valve stroke and open the shortcoming of duration, shock problem to valve retainer when solving air valve drop；A kind of actuated by cams formula hydraulic engine valve is provided to control device.
For solving above-mentioned technical problem, this utility model adopts the following technical scheme that realization, and accompanying drawings is as follows:
A kind of actuated by cams formula hydraulic engine valve controls device, including hydraulic piston valve group A, valve duration phase controlling organization and air valve drop buffer gear B, valve lift control mechanism, check valve I 4, oil pump 6 and fuel tank I 7, valve lift control mechanism includes check valve II 10 and cam I 11；Cam I 11 is arranged on the upper surface of spring base IV 47；
Spring base IV 47 lower end is fixing with the spring in check valve II 10 to be connected, and upper end is undertaken spacing by snap ring 48.And the upper surface of spring base IV 47 contacts with cam I 11.Spring upper end in check valve II 10 is limited by spring base IV 47, and lower end is limited by the steel ball in check valve II 10.
Fuel tank I 7 communicates with check valve I 4, check valve II 10 respectively；
Oil pump 6 is arranged between check valve I 4 and fuel tank I 7；
Hydraulic piston valve group A communicates with check valve I 4, check valve II 10 respectively；
Hydraulic piston valve group A is communicated by oil pipe I 1, oil pipe II 2 with valve duration phase controlling organization and air valve drop buffer gear B.
Hydraulic piston valve group A described in technical scheme is made up of valve 12, cotter seat I 13, spring I 14, cotter seat II 15, piston bush 16, shell I 17, joint tongue groove 18, joint tongue 19, spring II 20, cam II 21, spring base III 22, piston rod I 23, piston I 24, piston II 25, piston rod II 26 and plunger shaft 43；
Cam II 21 is arranged on spring base III 22 upper surface；
Piston bush 16 is provided with hole I 40, hole II 41 and hole III 42, piston I 24 and piston II 25 and is placed in piston bush 16, is slidably connected with piston bush 16 inwall, and plunger shaft 43 is the chamber portion between piston I 24, piston II 25 and piston bush 16；
Piston rod II 26 is fixedly connected with cotter seat I 13 and cotter seat II 15, spring I 14 is sleeved on piston rod II 26, and it is arranged between cotter seat I 13 and cotter seat II 15, piston rod II 26 upper end is connected through the centre bore bottom piston bush 16 and piston II 25 lower end are fixing, and piston rod II 26 lower end is fixing with valve 12 to be connected；
Piston rod I 23 upper end is fixing with spring base III 22 to be connected, and lower end is connected through joint tongue 19 and joint tongue groove 18 are fixing with piston I 24, and spring II 20 is sleeved on piston rod I 23, and is arranged between spring base III 22 and joint tongue groove 18；
Joint tongue 19 is fixing with in the middle part of piston rod I 23 to be connected, and joint tongue 19 and piston rod I 23 can slide in joint tongue groove 18；
Shell I 17 is fixing with piston bush 16 to be connected, and shell I 17 is fixing with joint tongue groove 18 to be connected.
The controlling organization of valve duration phase described in technical scheme and air valve drop buffer gear B are made up of motor 27, shell II 28, axle sleeve 29, helicla flute 30, axle 31, gear I 32, spline 33, oil leak hole I 34, fuel tank II 35, fuel feed hole I 36, fuel feed hole II 37, oil leak hole II 38, sleeve 44, gear II 45 and the axle collar 46；
Fuel feed hole I 36 and fuel feed hole II 37 are arranged on axle sleeve 31；Oil pipe I 1 one end is fixed in the hole II 41 of hydraulic piston valve group A, and the other end is fixed in fuel feed hole II 37；Oil pipe II 2 one end is fixed in the hole III 42 of hydraulic piston valve group A, and the other end is fixed in fuel feed hole I 36；
Shell 28 is fixing with axle sleeve 29 to be connected；Axle 31 rotates in axle sleeve 29, and axle sleeve 29 provides guide effect for axle 31；
Helicla flute 30 is arranged on axle 31, and helicla flute 30 is provided with oil leak hole I 34；
Oil leak hole II 38 one end connection oil leak hole I 34, the other end is communicated with fuel tank II 35 by axle 31 end；
Motor 27 is connected with gear II 45, and gear I 32 is connected with axle 31 by spline 33, and sleeve 44 and gear II 45 are meshed, and sleeve 44 is enclosed within axle 31, and the axial two ends of sleeve 44 are fixed by the axle collar 46, and axle 31 can rotate in sleeve 44.
It is provided with cleaner 5 between fuel tank I 7 described in technical scheme and oil pump 6.
Compared with prior art the beneficial effects of the utility model are:
1, can to realize valve stroke, valve closing time and unlatching duration variable for this utility model, and has the effect that air valve drop is cushioned.
2, this utility model simple in construction, it is possible to change valve stroke flexibly and open the duration.
3, this utility model can improve the charging efficiency of electromotor, improves dynamic property and the economy of electromotor.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, this utility model is further described:
Fig. 1 is the structural representation that actuated by cams formula hydraulic engine valve described in the utility model controls device；
Fig. 2 is the structural representation that actuated by cams formula hydraulic engine valve described in the utility model controls the hydraulic piston valve group of device；
Fig. 3 is that actuated by cams formula hydraulic engine valve described in the utility model controls the valve duration phase controlling organization of device and the structural representation of air valve drop buffer gear；
Fig. 4 is the sectional structure schematic diagram in C C direction in Fig. 3；
Fig. 5 is the sectional view of Fig. 3 axis 31；
Fig. 6 is the left view in Fig. 5；
Fig. 7 is the sectional structure schematic diagram in D D direction in Fig. 3；
Fig. 8 is the structural representation that actuated by cams formula hydraulic engine valve described in the utility model controls the valve lift control mechanism of device；
nullWherein: A. hydraulic piston valve group、B. valve duration phase controlling organization and air valve drop buffer gear、1. oil pipe I、2. oil pipe II、3. oil pipe III、4. check valve I、5. cleaner、6. oil pump、7. fuel tank I、8. oil pipe IV、9. oil pipe V、10. check valve II、11 cams I、12. valve、13. cotter seat I、14. spring I、15. cotter seat II、16. piston bush、17. shell I、18. joint tongue groove、19. joint tongue、20. spring II、21. cam II、22. spring base III、23. piston rod I、24. piston I、25. piston II、26. piston rod II、27. motor、28. shell II、29. axle sleeve、30. helicla flute、31. axle、32. gear I、33. spline、34. oil leak hole I、35. fuel tank II、36. fuel feed hole I、37. fuel feed hole II、38. oil leak hole II、39. oil pipe VI、40. hole I、41. hole II、42. hole III、43. plunger shaft、44. sleeve、45. gear II、46. the axle collar、47. spring base IV、48. snap ring.
Detailed description of the invention
Below in conjunction with accompanying drawing, this utility model is explained in detail:
Consulting Fig. 1, this utility model is made up of hydraulic piston valve group A, valve duration phase controlling organization and air valve drop buffer gear B, valve lift control mechanism (including check valve II 10, cam I 11), oil pipe I 1, oil pipe II 2, oil pipe III 3, check valve I 4, cleaner 5, oil pump 6, fuel tank I 7, oil pipe IV 8, oil pipe V 9, fuel tank II 35；
Fuel tank I 7 and fuel tank II 35 are common fuel tank, are used for storing hydraulic oil.
Cleaner 5 is arranged between fuel tank I 7 and oil pump 6, and its hydraulic oil acting as sucking oil pump 6 is filtered, it is ensured that in the cleaning of hydraulic oil in whole feed system.
The Main Function of check valve I 4 is high-pressure system to be separated with low-pressure system, can be the timely repairing of high-pressure system, also can prevent the hydraulic oil in high-pressure system from entering low-pressure system.
The Main Function of check valve II 10 is the pretightning force by adjusting spring, adjusts the oil pressure in plunger shaft 43 further, to change the maximum lift of valve 12.
Cam I 11 is arranged on the upper surface of spring base IV 47, and cam I 11 provides power for valve lift control mechanism, changes the pretightning force of spring in check valve II 10.
Spring base IV 47 lower end is fixing with the spring in check valve II 10 to be connected, and upper end is undertaken spacing by snap ring 48.And the upper surface of spring base IV 47 contacts with cam I 11.Spring upper end in check valve II 10 is limited by spring base IV 47, and lower end is limited by the steel ball in check valve II 10.
Oil pipe IV 8 port of export is placed in fuel tank I 7, and oil pipe IV 8 arrival end is connected to check valve II 10；Oil pipe VI 39 entrance is placed in fuel tank I 7, and oil pipe VI 39 port of export is connected to check valve I 4, oil pump 6 of connecting in oil pipe VI 39；Oil pipe V 9 one end is connected to check valve II 10, and the other end is connected to oil pipe III 3；
Consulting Fig. 1, Fig. 2, oil pipe III 3 one end is fixed in the hole I 40 of hydraulic piston valve group A, and the other end is connected to check valve I 4 and check valve II 10；Oil pipe I 1 one end is fixed in the hole II 41 of hydraulic piston valve group A, and the other end is fixed in fuel feed hole II 37；Oil pipe II 2 one end is fixed in the hole III 42 of hydraulic piston valve group A, and the other end is fixed in fuel feed hole I 36.
Consulting Fig. 2, hydraulic piston valve group A is made up of valve 12, cotter seat I 13, spring I 14, cotter seat II 15, piston bush 16, shell I 17, joint tongue groove 18, joint tongue 19, spring II 20, cam II 21, spring base III 22, piston rod I 23, piston I 24, piston II 25, piston rod II 26 and plunger shaft 43；
Cam II 21 is arranged on spring base III 22 upper surface；Cam II 21 provides power for variable valve actuator for air, drives valve 12 to open and close；
Wherein piston bush 16 is provided with hole I 40, hole II 41 and hole III 42, piston I 24 and piston II 25 are placed in piston bush 16, it is slidably connected with piston bush 16 inwall, plunger shaft 43 is the chamber portion between piston I 24, piston II 25 and piston bush 16, and provides guide effect for piston I 24, piston II 25 in the slip of piston bush 16 inwall.
Piston rod II 26 is connected with cotter seat I 13 and cotter seat II 15, it is cased with valve spring I 14 again, piston rod II 26 upper end is affixed through the centre bore bottom piston bush 16 and piston II 25 lower end, and valve spring I 14 upper and lower side is spacing by cotter seat I 13 and cotter seat II 15 respectively.Piston rod I 23 upper end is fixed in spring base III 22, lower end is fixed in piston I 24 through joint tongue 19 and joint tongue groove 18, spring II 20 upper and lower side is respectively by spacing with joint tongue groove 18 bottom spring base III 22, shell I is affixed with piston bush 16, cam II 21 drives piston I 24 descending, oil pressure in high-pressure system rises, and promotes valve piston 25 to overcome the pretightning force of valve spring I 14, promotes valve 12 to open.
Spring I 14 upper and lower side is spacing by cotter seat I 13 and cotter seat II 15 respectively.
The Main Function of spring I 14 is to ensure that valve 12 is taken a seat in time.
Piston bush 16 can provide guiding for the motion of piston I 24 and piston II 25, and piston bush 16 has hole I 40, hole II 41 and hole III 42.
Shell I 17 and piston bush 16 and joint tongue groove 18 are all affixed.
In the middle part of joint tongue 19 and piston rod I 23 affixed, joint tongue 19 and piston rod I 23 can slide in joint tongue groove 18.
Spring II 20 upper and lower side is spacing by the upper end of joint tongue groove 18 and spring base III 22 respectively, and the effect of spring II 20 is to ensure that when cam II 21 declines, spring base III 22 contacts with cam II 21 all the time.
Piston rod I 23 lower end is affixed with piston I 24, and upper end is affixed with spring base II 22.
Piston rod II 26 upper end is affixed with piston I 25, and piston rod II 26 lower end is affixed with valve 12.
Cam II 21 is different from general valve cam shape line, owing to need not valve directly be controlled cam, therefore the method for high power need not be adopted to realize the buffering of valve is taken a seat, concrete cam face consults Fig. 2, and the two ends up and down of cam II 21 adopt circular arc to carry out excessively.
Cam II 21 is mainly whole variable valve actuator for air and provides power, drives valve 12 to open and close.
Oil pump 6 is common gear pump, the hydraulic oil of 0.2--0.5MPa is provided for system, thus ensureing the whole system demand for hydraulic oil, when cam II 21 is in descending branch, piston I 24 starts to fall after rise, fluid pressure in high-pressure system is it would appear that higher or lower than the situation of low-pressure system pressure, when hydraulic coupling is higher than low-pressure system pressure, check valve II 10 is closed, when hydraulic coupling is lower than low-pressure system pressure, check valve I 4 is opened, and the hydraulic oil in low-pressure system enters high-pressure system by check valve I 4 and hole I 40.
Consult Fig. 1, Fig. 3, Fig. 4, Fig. 5, valve duration phase controlling organization and air valve drop buffer gear B to be made up of motor 27, shell II 28, axle sleeve 29, helicla flute 30, axle 31, gear I 32, spline 33, oil leak hole I 34, fuel tank II 35, fuel feed hole I 36, fuel feed hole II 37, oil leak hole II 38, sleeve 44, gear II 45 and the axle collar 46；
Axle 31 is rotated by spline 33 by gear I 32, and sleeve 44 and gear II 45 are that engagement, its axis perpendicular, and the axial location of sleeve 44 are fixed by the axle collar 46, and axle 31 can rotate freely in sleeve 44.When motor 27 driven gear II 45 rotates, sleeve 44 and the common axially-movable of axle 31 can be realized by the engagement of sleeve 44 and gear II 45.Its middle gear I 32 rotation direction is right view clockwise direction.
Motor 27 is by the engagement of sleeve 44 and gear II 45, it may be achieved sleeve 44 and the common axially-movable of axle 31, to change valve-opening time.
Shell 28 is affixed with axle sleeve 29；Axle 31 rotates in axle sleeve 29, and axle sleeve 29 also provides guide effect for axle 31.
Helicla flute 30 is opened on axle 31, is provided the passage of draining by fuel feed hole I 36 and fuel feed hole II 37 for hydraulic oil, by changing the relative position of helicla flute 30 and fuel feed hole I 36, thus it is possible to vary valve 12 start-up time and opening time, and simple in construction, easy to control；Meanwhile, in groove, oil leak hole I 34 is had.
Gear I 32 is provided power to rotate by bent axle, is rotated by spline 33 band moving axis 31.
Fuel feed hole I 36 and fuel feed hole II 37 are the hole opened on axle sleeve 31, when its Main Function is to carry out pressure release for the hydraulic oil in high-pressure system, it is provided that passage.
Oil leak hole II 38 one end connection oil leak hole I 34, the other end is flowed into fuel tank II 35 by axle 31 end.
Oil leak hole II 38 one end connection oil leak hole I 34, the other end is communicated with fuel tank II 35 by axle 31 end.When hydraulic oil emptying, hydraulic oil flows into oil leak hole II 38 by oil leak hole I 34, then is flowed out by the other end of oil leak hole II 38, subsequently into fuel tank II 35；
Sleeve 44 is enclosed within axle 31, and two ends are carried out axial limiting by the axle collar 46, it is ensured that sleeve 44 and axle 31 do not have relative motion in the axial direction.
Gear II 45 is connected with motor 27, and gear is meshed with sleeve 44.It act as the axially-movable that the rotary motion of motor 27 becomes sleeve 44, carries out axially-movable being further driven to axle 31.
In valve duration phase controlling organization and air valve drop buffer gear B, fuel feed hole I 36 and the fuel feed hole II 37 position on axle sleeve 29 present certain phase angle, to ensure to make piston 43 be in air-tight state between primary and secondary draining for some time, better carry out buffering of taking a seat.
Hydraulic piston valve group A mesopore II 41 and hole III 42 also in a distance, also to ensure to exist between primary and secondary draining certain phase angle, it is achieved steadily taking a seat of valve.
Valve duration phase controlled work process in valve duration phase controlling organization and air valve drop buffer gear B:
First hole I 40, hole II 41, hole III 42 are turned off, and the piston I 24 of cam II 21 driving hydraulic piston valve group A is descending, and the oil pressure in high-pressure system rises, and promote hydraulic valve piston II 25 to overcome spring I 14 to promote valve 12 to open.Now, owing to helicla flute 30 does not connect with fuel feed hole I 36 and fuel feed hole II 37, therefore the hydraulic oil in plunger shaft 43 is in sealing state, and valve stroke is maintained.When motor 27 by sleeve 44, gear II 45 and the axle collar 46, adjust the axial location of axle 31 so that the moment that helicla flute 30 is connected with fuel feed hole I 36 and fuel feed hole II 37 can shift to an earlier date or delayed.When the connection moment shifts to an earlier date, the draining moment, the persistent period of valve opening shortened in advance；When the connection moment is delayed, the draining moment is delayed, and the persistent period of valve opening is elongated.By this kind of method and then the size adjusting draining phase angle, it is achieved the unlatching persistent period of valve 12 is taken a seat phase place and valve 12 is controlled.
In valve duration phase controlling organization and air valve drop buffer gear B, air valve drop cushions controlled work process:
Valve falls the first stage after rise: when valve 12 starts to fall after rise the initial stage, due to valve stroke relatively big (being generally higher than 2mm), the position of piston II 25 fails to hide lateral aperture I 40, hole III 42 and hole II 41, when gear I 32 continues to rotate and drive the rotation of axle 31, helicla flute 30 rotates to when communicating with fuel feed hole I 36, oil in plunger shaft 43 is now by oil leak hole I 34, fuel tank II 35 is flowed into via oil leak hole II 38, the flow direction of hydraulic oil now is: plunger shaft 43 hole III 42 oil pipe II 2 fuel feed hole I 36 helicla flute 30 oil leak hole I 34 oil leak hole II 38 fuel tank II 35；Along with draining process, valve 12 is taken a seat, and gradually hole II 42 is hidden, form variable restrictor passage, the circulation area of this variable restrictor passage reduces with the reduction of valve stroke, form strong throttling action, make valve crash speed start to slow down, valve close to valve retainer but without taking a seat completely；The diameter of this process mesopore III 42, oil pipe II 2 and fuel feed hole I 36 is all relatively larger, belongs to the main draining stage.
Valve falls second stage after rise: along with the helicla flute 30 that further rotates of axle 31 does not communicate with fuel feed hole I 36, the oil in plunger shaft 43 carries out again airtight, and valve 12 is up to be compressed again to the oil in plunger shaft 43, and valve crash speed is greatly reduced.
Valve falls the phase III after rise: when axle 31 further rotates, helicla flute 30 connects with fuel feed hole 37, in plunger shaft 43, remaining oil is now again by oil leak hole I 34, flowing into fuel tank II 35 via oil leak hole II 38, the flow direction of hydraulic oil now is: plunger shaft 43 hole I 40 oil pipe I 1 fuel feed hole II 37 helicla flute 30 oil leak hole I 34 oil leak hole II 38 fuel tank II 35；Along with draining process, valve 12 continues to take a seat, and gradually hole II 41 is hidden, forming variable restrictor passage again, the circulation area of this variable restrictor passage reduces with the reduction of valve stroke, and the cross section of hole I 40, oil pipe I 1 and fuel feed hole II 37 is also less, throttling action can be formed, make valve crash speed start to slow down, it is achieved valve is taken a seat smoothly completely, complete once complete valve 12 closing process；This process belongs to time draining stage.
Valve lift control mechanism is made up of check valve II 10 and cam I 11；First hole I 40, hole II 41, hole III 42 are turned off, the piston I 24 of cam II 21 driving valve tappet group B is descending, oil pressure in high-pressure system rises, hydraulic valve piston II 25 is promoted to overcome valve spring I 14 to promote valve 12 to open,, check valve II 10 can pass through to control pressure in plunger shaft 43, controls the maximum lift of valve 12, the initial tension of spring of check valve II 10 can pass through the rotation of motor band moving cam I 11 and be adjusted, to change the pressure that check valve is opened.
In conjunction with each assembly of this utility model and installation site relation thereof, the technical scheme that this utility model actuated by cams formula hydraulic engine valve controls device is as follows:
1. when electromotor is in low speed Smaller load, induction air flow ratio is low, and fluid inertial flow is little, less valve 12 lift and shorter valve-opening time should be adopted, be conducive to strengthening In Cylinder Flow, improve burning velocity, increase low engine speed moment of torsion, improve cold start-up and reduce oil consumption.As it is shown in figure 1, by the position of adjustment cam I 11, reduce the initial tension of spring in check valve II 10 further, reduce the oil pressure in plunger shaft 43 to reduce the lift of valve 12.Simultaneously, motor 27 is by sleeve 44, gear II 45 and the axle collar 46, band moving axis 31 carries out axially-movable, helicla flute 30 also can change with the fuel feed hole I 36 on axle sleeve 29 and fuel feed hole II 37 phase place, and then adjust the size at draining phase angle, it is achieved the control to air valve drop phase place and valve duration.
2., when electromotor is in big load at a high speed, induction air flow ratio is big, and fluid inertial flow is strong, bigger valve 12 lift and longer valve-opening time should be adopted, be conducive to strengthening In Cylinder Flow, improve burning velocity, increase low engine speed moment of torsion, improve cold start-up and reduce oil consumption.As it is shown in figure 1, by the position of adjustment cam I 11, improve the initial tension of spring in check valve II 10 further, improve the oil pressure in plunger shaft 43 to increase the lift of valve 12.Simultaneously, motor 27 is by sleeve 44, gear II 45 and the axle collar 46, band moving axis 31 carries out axially-movable, helicla flute 30 also can change with the fuel feed hole I 36 on axle sleeve 29 and fuel feed hole II 37 phase place, and then adjust the size at draining phase angle, it is achieved the control to air valve drop phase place and valve duration.
Work process of the present utility model is divided into the following two stage:
1. valve 12 open stage, this stage hole I 40, hole II 41, hole III 42 are turned off, the piston I 24 of cam II 21 driving valve tappet group B is descending, oil pressure in high-pressure system rises, hydraulic valve piston II 25 is promoted to overcome valve spring I 14 to promote valve 12 to open, check valve II 10 can pass through to control pressure in plunger shaft 43, controls the maximum lift of valve 12.
2. valve 12 falls the stage after rise, this stage along with gear I 32 rotation, drive the rotation of axle 31, when helicla flute 30 rotates to and communicates with fuel feed hole I 36, oil in plunger shaft 43 is now by oil leak hole I 34, via oil leak hole II 38 flow into fuel tank II 35, valve 12 is taken a seat, valve close to valve retainer but without taking a seat completely；Simultaneously along with the helicla flute 30 that further rotates of axle 31 does not communicate with fuel feed hole I 36, the oil in plunger shaft 43 carries out again airtight, and valve 12 is up to be compressed again to the oil in plunger shaft 43, and valve crash speed is greatly reduced；When axle 31 further rotates, helicla flute 30 connects with fuel feed hole 37, and in plunger shaft 43, remaining oil is now again by oil leak hole I 34, flows into fuel tank II 35 via oil leak hole II 38, valve is taken a seat slowly completely, completes once complete valve 12 opening-closing process.
Claims (4)
1. an actuated by cams formula hydraulic engine valve controls device, including hydraulic piston valve group (A), valve duration phase controlling organization and air valve drop buffer gear (B), valve lift control mechanism, check valve I (4), oil pump (6) and fuel tank I (7), it is characterised in that:
Valve lift control mechanism includes check valve II (10) and cam I (11)；Cam I (11) is arranged on the upper surface of spring base IV (47), and spring base IV (47) lower end is fixing with the spring in check valve II (10) to be connected；
Fuel tank I (7) communicates with check valve I (4), check valve II (10) respectively；
Oil pump (6) is arranged between check valve I (4) and fuel tank I (7)；
Hydraulic piston valve group (A) communicates with check valve I (4), check valve II (10) respectively；
Hydraulic piston valve group (A) is communicated by oil pipe I (1), oil pipe II (2) with valve duration phase controlling organization and air valve drop buffer gear (B).
2. a kind of actuated by cams formula hydraulic engine valve according to claim 1 controls device, it is characterised in that:
Described hydraulic piston valve group (A) is by valve (12), cotter seat I (13), spring I (14), cotter seat II (15), piston bush (16), shell I (17), joint tongue groove (18), joint tongue (19), spring II (20), cam II (21), spring base III (22), piston rod I (23), piston I (24), piston II (25), piston rod II (26) and plunger shaft (43) composition；
Cam II (21) is arranged on spring base III (22) upper surface；
Piston bush (16) is provided with hole I (40), hole II (41) and hole III (42), piston I (24) and piston II (25) are placed in piston bush (16), being slidably connected with piston bush (16) inwall, plunger shaft (43) is piston I (24), chamber portion between piston II (25) and piston bush (16)；
Piston rod II (26) is fixedly connected with cotter seat I (13) and cotter seat II (15), spring I (14) is sleeved on piston rod II (26), and it is arranged between cotter seat I (13) and cotter seat II (15), piston rod II (26) upper end is connected through the centre bore bottom piston bush (16) and piston II (25) lower end are fixing, and piston rod II (26) lower end is fixing with valve (12) to be connected；
Piston rod I (23) upper end is fixing with spring base III (22) to be connected, lower end is connected through joint tongue (19) and joint tongue groove (18) are fixing with piston I (24), spring II (20) is sleeved on piston rod I (23), and is arranged between spring base III (22) and joint tongue groove (18)；
Joint tongue (19) is fixing with piston rod I (23) middle part to be connected, and joint tongue (19) and piston rod I (23) can slide in joint tongue groove (18)；
Shell I (17) is fixing with piston bush (16) to be connected, and shell I (17) is fixing with joint tongue groove (18) to be connected.
3. a kind of actuated by cams formula hydraulic engine valve according to claim 1 controls device, it is characterised in that:
Described valve duration phase controlling organization and air valve drop buffer gear (B) are made up of motor (27), shell II (28), axle sleeve (29), helicla flute (30), axle (31), gear I (32), spline (33), oil leak hole I (34), fuel tank II (35), fuel feed hole I (36), fuel feed hole II (37), oil leak hole II (38), sleeve (44), gear II (45) and the axle collar (46)；
Fuel feed hole I (36) and fuel feed hole II (37) are arranged on axle sleeve (31)；Oil pipe I (1) one end is fixed in the hole II (41) of hydraulic piston valve group A, and the other end is fixed in fuel feed hole II (37)；Oil pipe II (2) one end is fixed in the hole III (42) of hydraulic piston valve group (A), and the other end is fixed in fuel feed hole I (36)；
Shell (28) is fixing with axle sleeve (29) to be connected；Axle (31) rotates in axle sleeve (29), and axle sleeve (29) provides guide effect for axle (31)；
Helicla flute (30) is arranged on axle (31), and helicla flute (30) is provided with oil leak hole I (34)；
Oil leak hole II (38) one end connection oil leak hole I (34), the other end is communicated with fuel tank II (35) by axle (31) end；
Motor (27) is connected with gear II (45), gear I (32) is connected with axle (31) by spline (33), sleeve (44) and gear II (45) are meshed, sleeve (44) is enclosed within axle (31), the axial two ends of sleeve (44) are fixed by the axle collar (46), and axle (31) can rotate in sleeve (44).
4. a kind of actuated by cams formula hydraulic engine valve according to claim 1 controls device, it is characterised in that:
Cleaner (5) it is provided with between fuel tank I (7) and oil pump (6).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620173009.7U CN205400837U (en) | 2016-03-07 | 2016-03-07 | Cam drive type engine hydraulic pressure gas door control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620173009.7U CN205400837U (en) | 2016-03-07 | 2016-03-07 | Cam drive type engine hydraulic pressure gas door control device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205400837U true CN205400837U (en) | 2016-07-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620173009.7U Withdrawn - After Issue CN205400837U (en) | 2016-03-07 | 2016-03-07 | Cam drive type engine hydraulic pressure gas door control device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205400837U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105604625A (en) * | 2016-03-07 | 2016-05-25 | 吉林大学 | Cam-driving engine hydraulic valve control device |
| CN110782683A (en) * | 2019-12-04 | 2020-02-11 | 唐山学院 | Traffic signal lamp capable of automatically controlling and adjusting time |
-
2016
- 2016-03-07 CN CN201620173009.7U patent/CN205400837U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105604625A (en) * | 2016-03-07 | 2016-05-25 | 吉林大学 | Cam-driving engine hydraulic valve control device |
| CN105604625B (en) * | 2016-03-07 | 2017-12-12 | 吉林大学 | Actuated by cams formula hydraulic engine valve control device |
| CN110782683A (en) * | 2019-12-04 | 2020-02-11 | 唐山学院 | Traffic signal lamp capable of automatically controlling and adjusting time |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20160727 Effective date of abandoning: 20171212 |