CN210396836U - Electro-hydraulic control device for valve timing - Google Patents
Electro-hydraulic control device for valve timing Download PDFInfo
- Publication number
- CN210396836U CN210396836U CN201921010170.2U CN201921010170U CN210396836U CN 210396836 U CN210396836 U CN 210396836U CN 201921010170 U CN201921010170 U CN 201921010170U CN 210396836 U CN210396836 U CN 210396836U
- Authority
- CN
- China
- Prior art keywords
- tappet
- spring
- valve
- way valve
- sleeve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Abstract
The utility model discloses an electro-hydraulic control device for valve timing, which comprises a hydraulic tappet, a distribution cam, a rocker arm roller, a valve assembly, a lubricating oil circuit, an oil return circuit and a solenoid valve, wherein the valve assembly comprises a valve spring and a valve; the valve advance angle and the valve retard angle can be independently adjusted only by changing the on-off time of the electromagnetic valve according to different working conditions of the engine, so that the engine can respectively obtain the optimal valve advance angle and the optimal valve retard angle under different working conditions, and the gas distribution timing requirements of the engine under different working conditions are met; the valve advance angle and the valve retard angle can be independently and accurately adjusted in one cycle; the lag angle adjusting range is large, the engine efficiency is improved, the power performance is improved, and energy conservation and emission reduction are realized.
Description
Technical Field
The utility model relates to an engine technical field relates to an electro-hydraulic regulation and control device in valve timing particularly.
Background
At present, in a cam-driven valve actuating system with a hydraulic tappet, the hydraulic tappet is used for automatically compensating a clearance caused by dimensional change of a valve and a transmission system due to thermal expansion, manufacturing error, abrasion and the like, reducing impact and improving motion stability, but does not have a valve timing adjusting function.
The variable valve timing technology can adjust the valve timing parameters according to the actual working conditions of the engine to meet the distribution requirements of different working conditions, thereby improving the dynamic characteristics of the engine, improving the fuel economy and reducing the emission of harmful gases. Currently, the following methods are mainly used for adjusting the variable valve timing: 1) each valve corresponds to a cam group consisting of a plurality of different cams, and the movement of the different cams is changed according to different rotating speeds of the engine to control the valve so as to realize the valve timing adjustment, so that the method only can ensure that the engine obtains the optimal valve timing of the cam profile in the cam group corresponding to the rotating speed and can not realize the stepless adjustment of the valve timing; 2) the valve timing is adjusted by changing the relative angle between the distribution camshaft and the engine crankshaft, and the valve opening continuous angle is not changed, so that the valve lead angle is increased and the valve lag angle is reduced by the same angle; conversely, increasing the valve retardation angle necessarily reduces the valve advance angle by the same angle. Therefore, the adjusting method cannot simultaneously meet the adjusting requirements of the valve advance angle and the valve retard angle under different working conditions of the engine. 3) The electromagnetic valve is directly driven, and the technology is flexible in adjustment, but has poor high-speed response, high energy consumption and large impact, so that the technology cannot well meet the gas distribution requirement of high rotating speed of an engine. In conclusion, the existing variable valve timing adjusting system cannot well meet the air distribution requirements of the engine at different rotating speeds, so that the improvement degree of the dynamic property, the fuel economy and the emission reduction of the engine is limited.
Disclosure of Invention
An object of the utility model is to provide a simple structure can realize the original clearance compensation function of hydraulic tappet and can carry out the electro-hydraulic regulation and control device of valve advance angle and lag angle according to the different operating modes of engine again, can overcome prior art's not enough.
In order to achieve the above object, the utility model provides a following technical scheme: a hydraulic regulation and control device for valve timing comprises a hydraulic tappet, a distribution cam, a rocker arm roller, a valve assembly, a lubricating oil path, an oil return path and an electromagnetic valve, wherein the valve assembly comprises a valve spring and a valve.
A rocker roller is arranged in the middle of the rocker, the hydraulic tappet and the valve assembly are respectively arranged at two ends of the same side of the rocker, a distribution cam is arranged on the opposite side surface of the rocker 3, and the working surface of the distribution cam is contacted with the outer circular surface of the rocker roller;
the hydraulic tappet comprises a tappet sleeve, a tappet one-way valve core, a tappet one-way valve spring seat, a tappet spring, a follow-up buffer sleeve, a buffer sleeve clamp spring, a tappet clamp spring, a buffer sleeve one-way valve core, a buffer sleeve one-way valve spring and a buffer sleeve spring;
the tappet is arranged in the tappet sleeve, and the tappet clamp spring is arranged in an annular groove of the tappet; the tappet one-way valve core is arranged in a one-way valve hole at the lower part of the tappet, the tappet one-way valve spring seat is arranged in a large step hole at the lower part of the tappet, the tappet one-way valve spring is arranged in the step hole of the tappet one-way valve spring seat, the upper end of the tappet one-way valve spring is contacted with the tappet one-way valve core, and the lower end of the tappet one-way valve spring is contacted with the bottom of the step hole of;
the tappet spring is arranged in a large step hole at the lower part of the tappet, the upper end of the tappet spring is in contact with the lower end surface of an annular step of the tappet one-way valve spring seat, and the lower end of the tappet spring is in contact with a clamping spring of the buffer sleeve;
the buffer sleeve snap spring is arranged in an annular groove at the upper part of the follow-up buffer sleeve, and the follow-up buffer sleeve is arranged in a step hole at the lower part of the tappet sleeve;
the buffer sleeve spring is arranged in the lower inner hole of the tappet sleeve, the lower end of the buffer sleeve spring is contacted with the lower bottom hole of the tappet sleeve, and the upper end of the buffer sleeve spring is contacted with the lower end surface of the follow-up buffer sleeve;
the one-way valve core of the buffer sleeve is arranged in the one-way valve hole of the follow-up buffer sleeve, the one-way valve spring of the buffer sleeve is arranged in the one-way valve hole of the follow-up buffer sleeve, the lower end of the one-way valve spring of the buffer sleeve is contacted with the bottom hole at the lower part of the tappet sleeve, and the upper end of the one-way valve spring of the buffer sleeve is contacted with;
the upper part of the tappet sleeve is provided with a tappet sleeve oil hole connected with an engine lubricating oil path, and the lower part of the tappet sleeve is provided with a quick section throttling hole connected with an oil return path;
a tappet stepped shaft hole coaxial with the tappet is arranged in the tappet, and a radial tappet oil hole which is communicated with the tappet stepped shaft hole and is constantly communicated with an oil hole on the tappet sleeve is arranged at the upper part of the tappet;
the on-off of the oil return path is controlled by the on-off state of the electromagnetic valve.
Preferably, the profile of the air distribution cam is composed of a plurality of sections of curves, and the rear section of the return combined curve is provided with a concentric circular arc which has a radius larger than the radius of a basic circle of the air distribution cam and a size equal to the terminal lift value of the front section of the curve connected with the concentric circular arc.
Preferably, the tappet sleeve, the tappet one-way valve core spring seat and the follow-up buffer sleeve are coaxial; the pretightening force of the tappet spring is greater than the sum of the pretightening force of the buffer sleeve spring and the pretightening force of the buffer sleeve one-way valve spring, but is far less than the pretightening force of the valve spring.
Preferably, the distance between the lower end surface of the damper sleeve clamp spring and the upper end surface of the tappet clamp spring is variable from zero to a set maximum separation distance, and the maximum separation distance is set according to the sum of a valve opening size parameter determined by a cam curve and a maximum clearance size parameter to be compensated by the valve drive system when the valve is required to adjust the retardation angle before seating.
Preferably, the follow-up buffer sleeve is a step shaft, a step shaft hole is arranged in the follow-up buffer sleeve, a radial hole penetrating through the step shaft hole is arranged at the upper end of the follow-up buffer sleeve, and a throttling buffer inclined plane is arranged on the outer circular surface of a step shaft shoulder of the follow-up buffer sleeve.
Compared with the prior art, the utility model has simple structure and high integration level, and is easy to integrate with the prior engine equipped with a hydraulic tappet; the system is flexible to adjust and high in precision, and the valve advance angle and the valve retard angle can be independently adjusted only by changing the on-off time of the electromagnetic valve according to different working conditions of the engine, so that the engine can respectively obtain the optimal valve advance angle and the optimal valve retard angle under different working conditions, and the gas distribution timing requirements of the engine under different working conditions are met; the valve advance angle and the valve retard angle can be independently and accurately adjusted in one cycle; the adjusting range of the lag angle is large, when the adjusting range is used for an intake valve, the effective compression ratio of the engine can be adjusted and controlled in real time, the engine can work under the most reasonable effective compression ratio condition according to the current working condition, the efficiency is improved, the power performance is improved, and the energy is saved and the emission is reduced; when the valve is used for an exhaust valve, the real-time regulation and control of the coefficient of residual exhaust gas in a cylinder and an HCCI combustion mode can be easily realized, the system runs stably, the motion process and the seating velocity of the valve closing are the same and do not change along with the change of the rotating speed of an engine, and the seating impact of the valve is small.
Drawings
Fig. 1 is a schematic structural view of the present invention;
fig. 2 is a schematic view of a profile of a cam according to the present invention;
FIG. 3 is a schematic view of the motion curve of the valve of the present invention;
fig. 4 is the state schematic diagram of the middle hydraulic tappet of the present invention when adjusting the valve lag angle.
In the figure: 1. the hydraulic tappet comprises a hydraulic tappet, 1.1, a tappet sleeve, 1.2, a tappet, 1.3, a tappet one-way valve core, 1.4, a tappet one-way valve spring, 1.5, a tappet one-way valve spring seat, 1.6, a tappet spring, 1.7, a follow-up buffer sleeve, 1.8, a buffer sleeve snap spring, 1.9, a tappet snap spring, 1.10, a buffer sleeve one-way valve core, 1.11, a buffer sleeve one-way valve spring, 1.12, a buffer sleeve spring, 1.13, a fast section throttling hole, 1.14, a throttling buffer inclined plane, 1.15, a radial hole, 1.16, a step shaft hole, 1.17, a tappet oil hole, 1.18, a tappet sleeve oil hole, 1.19, a low-speed throttling gap, 1.20, a tappet step shaft hole, 2, a cam, 3, a rocker arm, 4, a rocker arm roller, 5, an air valve oil return assembly, 5.1, an air valve, 6, a lubricating oil, 7, 8, and an electromagnetic valve.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
Referring to fig. 1-4, the present invention provides a technical solution: a hydraulic regulation and control device for valve timing comprises a hydraulic tappet 1, a distribution cam 2, a rocker arm 3, a rocker arm roller 4, a valve assembly 5, a lubricating oil path 6, an oil return path 7 and an electromagnetic valve 8. Wherein: the hydraulic tappet 1 comprises a tappet sleeve 1.1, a tappet 1.2, a tappet one-way valve core 1.3, a tappet one-way valve spring 1.4, a tappet one-way valve spring seat 1.5, a tappet spring 1.6, a follow-up buffer sleeve 1.7, a buffer sleeve snap spring 1.8, a tappet snap spring 1.9, a buffer sleeve one-way valve core 1.10, a buffer sleeve one-way valve spring 1.11 and a buffer sleeve spring 1.12, wherein the tappet 1.2 is arranged in a large step hole of the tappet sleeve 1.1, the tappet snap spring 1.9 is arranged in an annular groove of the tappet 1.2, the tappet one-way valve core 1.3 is arranged in a one-way valve hole at the lower part of the tappet 1.2, the tappet one-way valve spring seat 1.5 is arranged in a large step hole at the lower part of the tappet 1.2, the tappet one-way valve spring 1.4 is arranged in a large step hole of the tappet one-way valve spring seat 1.5, the upper end of the tappet one-way valve core 1.3 is in contact with the tappet one-way valve spring seat, the lower end of the tappet is in contact with the lower part of the tappet one-way valve spring seat 1.5, the, The lower end of the valve component 5 is contacted with a floating sleeve clamp spring 1.8, a buffer sleeve clamp spring 1.8 is arranged in an annular groove at the upper part of a follow-up buffer sleeve 1.7, the follow-up buffer sleeve 1.7 is arranged in a step hole at the lower part of a tappet sleeve 1.1, a buffer sleeve spring 1.12 is arranged in a lower inner hole of the tappet sleeve 1.1, the lower end of the buffer sleeve spring is contacted with a lower bottom hole of the tappet sleeve 1.1, the upper end of the buffer sleeve spring is contacted with the lower end surface of the follow-up buffer sleeve 1.7, a buffer sleeve one-way valve core 1.10 is arranged in a one-way valve hole of the follow-up buffer sleeve 1.7, the lower end of the buffer sleeve spring is contacted with a lower bottom hole of the tappet sleeve 1.1, and the upper end of the buffer sleeve one-way valve core 1.10 is contacted with the buffer sleeve one-way valve core; the rocker roller 4 is arranged in the middle of the rocker 3, the hydraulic tappet 1 and the valve component 5 are respectively arranged at two ends of the same side of the rocker 3, and the distribution cam 2 is arranged on the opposite side surfaces of the hydraulic tappet 1 and the valve component 5 on the rocker 3, and the working surface of the distribution cam is contacted with the outer circular surface of the rocker roller 4. The profile of the distribution cam 2 is composed of a plurality of sections of curves, and the rear section of the return combined curve is provided with a concentric circular arc which has a radius larger than the radius of a basic circle of the distribution cam and a size equal to the terminal lift value of the curve of the front section connected with the distribution cam. The tappet sleeve 1.1, the tappet 1.2, the tappet one-way valve core spring seat 1.5 and the follow-up buffer sleeve 1.7 are coaxial. The pretightening force of the tappet spring 1.6 is greater than the sum of the pretightening force of the buffer sleeve spring 1.12 and the pretightening force of the buffer sleeve one-way valve spring 1.11, but is far less than the pretightening force of the valve spring 5.1. The distance between the lower end surface of the buffer sleeve clamp spring 1.8 and the upper end surface of the tappet clamp spring 1.9 can be changed from zero to a set maximum separation distance, and the maximum separation distance is set according to the sum of the valve opening size parameter determined by a cam curve and the maximum clearance size parameter required to be compensated by a valve driving system when the valve needs to be subjected to lag angle adjustment before being seated. The upper part of the tappet sleeve 1.1 is provided with a tappet sleeve oil hole 1.18 connected with an engine lubricating oil circuit 6, and the lower part is provided with a fast section throttling hole 1.13 connected with an oil return circuit 7. The inner part of the tappet 1.2 is provided with a tappet stepped shaft hole 1.20 which is coaxial with the tappet 1.2, and the upper part is provided with a radial tappet oil hole 1.17 which is communicated with the tappet stepped shaft hole 1.20 and is communicated with the tappet sleeve oil hole 1.18 at any moment. The follow-up buffer sleeve 1.7 is a step shaft, a step shaft hole 1.16 is arranged in the follow-up buffer sleeve, a radial hole 1.15 which penetrates through the step shaft hole 1.16 is arranged at the upper end of the follow-up buffer sleeve, and a throttling buffer inclined plane 1.14 is arranged on the outer circular surface of a step shaft shoulder. The throttling clearance between the large outer circular surface of the follow-up buffer sleeve 1.7 and the installation inner hole of the tappet sleeve 1.1 is determined according to the speed requirement of the valve seating low-speed section by a fluid mechanics method. The on/off of the oil return path 7 is controlled by the on/off state of the solenoid valve 8.
The working process is as follows:
when the distribution cam 2 rotates clockwise and the base circle segment in the profile line CO range shown in fig. 2 contacts the rocker roller 4, the valve 5.2 is in a closed state under the action of the valve spring 5.1. At this time, the electromagnetic valve 8 is in a closed state, the tappet 1.2 is at the highest position of the current working condition under the combined action of the tappet spring 1.6 and the cushion sleeve spring 1.12, and the tappet 1.2 moves to the position where the cushion sleeve snap spring 1.7 is in contact with the tappet snap spring 1.8 as the pretightening force of the tappet spring 1.6 is greater than the sum of the pretightening forces of the cushion sleeve spring 1.12 and the cushion sleeve check valve spring 1.11, as shown in fig. 1. When the air distribution cam 2 continues to rotate to a point O, the contact part of the rocker arm roller 4 and the air distribution cam 2 starts to enter a lift section of the air distribution cam 2, the trend that the tappet 1.2 moves downwards under the action of the rocker arm 3 enables the oil pressure in an oil cavity at the lower part of the tappet 1.2 to be increased, the tappet one-way valve is in a closed state, and the downward movement trend of the tappet 1.2 is transmitted to the follow-up buffer sleeve 1.7 by the tappet spring 1.6 because the pretightening force of the tappet spring 1.6 is greater than the sum of the pretightening force of the buffer sleeve spring 1.12 and the pretightening force of the buffer sleeve one-way valve spring 1.11. Under the combined action of the oil pressure of the lower oil cavity of the tappet spring 1.6 and the oil pressure of the lower oil cavity of the tappet 1.2, the oil pressure of the lower oil cavity of the follow-up buffer sleeve 1.7 is higher than the oil pressure of the lower oil cavity of the tappet 1.2, and the one-way valve of the buffer sleeve is in a closed state. Neglecting the compressibility of oil, the hydraulic tappet 1 becomes a rigid body, the head of the tappet 1.2 of the hydraulic tappet 1 becomes the fulcrum of the rocker arm 3, and as the air distribution cam 2 continues to rotate, the valve 5.2 will be opened and opened to the maximum opening degree, such as the OH section of fig. 3. In this case, the maximum valve advance angle is obtained.
When the distribution cam 2 rotates clockwise and a base circle section in the profile line CO range shown in fig. 2 contacts with the rocker arm roller 4, the electromagnetic valve 8 is in a conducting state, when the distribution cam 2 rotates to a point O, the contact position of the rocker arm roller 4 and the distribution cam 2 starts to enter a lift section of the distribution cam 2, the tappet 1.2 moves downwards under the action of the rocker arm 3, oil in an oil cavity at the lower part of the tappet 1.2 flows back to an oil tank through the fast section throttling hole 1.13, the oil return circuit 7 and the one-way valve 8, and simultaneously under the action of the stroke flow resistance and the tappet spring force, the tappet one-way valve and the buffer sleeve one-way valve are both in a closing state, and the state continues until the electromagnetic valve 8 is closed at an arbitrary point G of the profile line OH section shown in fig. 2. After the electromagnetic valve 8 is closed, the hydraulic tappet 1 becomes a rigid body under the condition of neglecting the compressibility of oil, the head of the tappet 1.2 of the hydraulic tappet 1 becomes the fulcrum of the rocker arm 3, and the valve 5.2 is opened to the maximum opening degree along with the continuous rotation of the distribution cam 2, as shown in the GH section of fig. 3. Compared with the condition that the electromagnetic valve 8 is closed in advance before the air distribution cam 2 rotates to the point O, the opening position of the valve 5.2 is lagged, and the adjustment of the valve advance angle is realized. Therefore, the requirement of the valve advance angle of the engine can be met by adjusting the closing time of the electromagnetic valve 8 according to different engine speeds.
When the contact between the rocker roller 4 and the valve cam 2 is in the return stroke stage of the valve cam 2, the opening degree of the valve 5.2 is continuously reduced along with the reduction of the cam lift under the action of the valve spring 5.1. When the valve cam 2 rotates to the profile line a shown in fig. 2, the valve 5.2 also falls back to the lift at point a shown in fig. 3. At this time, if the electromagnetic valve 8 is not switched on, the oil in the inner cavity at the lower part of the tappet 1.2 cannot return to the oil tank through the oil return path 7 and the electromagnetic valve 8, the hydraulic tappet 1 is still a rigid whole, and when the distribution cam 2 rotates from the point of the profile a to the point B in fig. 2, the valve 5.2 keeps a certain opening degree and stops, as shown by a horizontal straight line segment AB in fig. 3; when the air distribution cam 2 rotates from the point of the profile line B to the point C in fig. 2, the valve 5.2 continues to fall back until it is closed, as indicated by the line BC in fig. 3. In this case, the maximum valve lag is obtained.
If the electromagnetic valve 8 is in a conducting state when the distribution cam 2 rotates to any point D of the profile AB section shown in fig. 2, the oil return path 7 is communicated with an oil path between an oil chamber at the lower part of the tappet 1.2 and an oil tank through the fast section throttling hole 1.13, and oil in the oil chamber at the lower part of the tappet 1.2 flows back to the oil tank through the fast section throttling hole 1.13, the oil return path 7 and the one-way valve 8. Meanwhile, the oil pressure of the oil in the oil chamber at the lower part of the tappet 1.2 begins to drop, the height of the tappet 1.2 also begins to drop, the valve 5.2 also begins to continue to drop under the action of the valve spring 5.1, and the movement speed of the valve 5.2 at this stage is controlled by the throttling hole 1.13 at the fast stage, as shown in the DE stage in fig. 3. When the lower edge of the inner hole of the tappet 1.2 descends to the throttling buffer inclined plane 1.14 of the follow-up buffer sleeve 1.7, oil above the throttling buffer inclined plane 1.14 can only flow through a low-speed throttling gap 1.19 between the inner hole of the tappet 1.2 and the follow-up buffer sleeve 1.7. The stroke of the fast section is determined by the size of the tappet 1.2 from the initial position of starting the downward movement to the position of the follow-up cushion sleeve 1.7 where the throttling cushion slope 1.14 plays a role of cushioning. As long as the proper size of the follow-up cushion sleeve 1.7 is set according to the use requirement, the starting position and the flow rate of the throttling can be controlled, the height descending speed of the tappet 1.2 is reduced, and the seating speed of the valve 5.2 is reduced at the same time and finally the valve is seated smoothly. Compared with the condition that the electromagnetic valve 8 is not switched on when the valve distribution cam 2 rotates at the section of the molded line AB, the valve 5.2 is closed in advance, and the valve lag angle is adjusted. Therefore, according to different engine speeds, the valve lag angle requirement of the engine can be met by adjusting the conduction time of the electromagnetic valve 8. After the valve 5.2 is seated, the valve spring force no longer acts on the tappet 1.2, and when the distribution cam 2 continues to rotate at the segment BC of fig. 2, the tappet 1.2 moves upward under the spring force of the tappet spring 1.6 and is always in contact with the rocker arm 3. In the process, the volume of the oil cavity at the lower part of the tappet 1.2 is increased, the pressure is reduced, the tappet one-way valve is opened, and the lubricating oil of the engine is supplemented to the oil cavity at the lower part of the tappet 1.2 through the one-way valve, so that preparation is made for the next cycle.
For the dimensional change of the valve driving system caused by manufacturing error, abrasion, expansion with heat and contraction with cold and the like, the engine rotates to the initial position when the base circle section within the molded line CO range shown in figure 2 contacts with the rocker roller 4 by the distribution cam 2 in each cycle, the tappet 1.2 automatically compensates with the gap as zero under the action of the lower tappet spring 1.6, and the follow-up buffer sleeve 1.7 automatically follows along with the change of the initial position of the tappet 1.2 by utilizing the limiting function between the buffer sleeve clamp spring and the tappet clamp spring.
In conclusion, the valve advance angle and the valve retard angle of the engine under different working conditions can be independently and accurately adjusted by reasonably adjusting the switching time of the electromagnetic valve 8 according to different working conditions of the engine.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (5)
1. The utility model provides a valve timing's electricity liquid regulation and control device, includes hydraulic tappet (1), distribution cam (2), rocking arm (3), rocking arm roller (4), valve module (5), lubricated oil circuit (6), oil return way (7) and solenoid valve (8), and this valve module (5) include valve spring (5.1) and valve (5.2), its characterized in that:
a rocker roller (4) is arranged in the middle of the rocker (3), the hydraulic tappet (1) and the valve assembly (5) are respectively arranged at two ends of the same side of the rocker (3), a distribution cam (2) is arranged on the opposite side surface of the rocker (3), and the working surface of the distribution cam is contacted with the outer circular surface of the rocker roller (4);
the hydraulic tappet (1) comprises a tappet sleeve (1.1), a tappet (1.2), a tappet one-way valve core (1.3), a tappet one-way valve spring (1.4), a tappet one-way valve spring seat (1.5), a tappet spring (1.6), a follow-up buffer sleeve (1.7), a buffer sleeve snap spring (1.8), a tappet snap spring (1.9), a buffer sleeve one-way valve core (1.10), a buffer sleeve one-way valve spring (1.11) and a buffer sleeve spring (1.12);
the tappet (1.2) is arranged in the tappet sleeve (1.1), and the tappet clamp spring (1.9) is arranged in an annular groove of the tappet (1.2); a tappet one-way valve core (1.3) is arranged in a one-way valve hole at the lower part of a tappet (1.2), a tappet one-way valve spring seat (1.5) is arranged in a large step hole at the lower part of the tappet (1.2), a tappet one-way valve spring (1.4) is arranged in the step hole of the tappet one-way valve spring seat (1.5), the upper end of the tappet one-way valve spring is contacted with the tappet one-way valve core (1.3), and the lower end of the tappet one-way valve spring is contacted with the bottom of the step hole of the tappet one-way valve spring seat (;
the tappet spring (1.6) is arranged in a large step hole at the lower part of the tappet (1.2), the upper end of the tappet spring is contacted with the lower end surface of an annular step of the tappet one-way valve spring seat (1.5), and the lower end of the tappet spring is contacted with the buffer sleeve clamp spring (1.8);
the buffer sleeve snap spring (1.8) is arranged in an annular groove at the upper part of the follow-up buffer sleeve (1.7), and the follow-up buffer sleeve (1.7) is arranged in a step hole at the lower part of the tappet sleeve (1.1);
the buffer sleeve spring (1.12) is arranged in the lower inner hole of the tappet sleeve (1.1), the lower end of the buffer sleeve spring is contacted with the lower bottom hole of the tappet sleeve (1.1), and the upper end of the buffer sleeve spring is contacted with the lower end surface of the follow-up buffer sleeve (1.7);
the one-way valve core (1.10) of the buffer sleeve is arranged in the one-way valve hole of the follow-up buffer sleeve (1.7), the one-way valve spring (1.11) of the buffer sleeve is arranged in the one-way valve hole of the follow-up buffer sleeve (1.7), the lower end of the one-way valve spring is contacted with the bottom hole at the lower part of the tappet sleeve (1.1), and the upper end of the one-way valve spring is contacted with the one-way valve core (1.10) of the buffer sleeve;
the upper part of the tappet sleeve (1.1) is provided with a tappet sleeve oil hole (1.18) connected with an engine lubricating oil path (6), and the lower part of the tappet sleeve oil hole is provided with a fast section throttling hole (1.13) connected with an oil return path (7);
a tappet stepped shaft hole (1.20) coaxial with the tappet (1.2) is arranged in the tappet (1.2), and the upper part of the tappet (1.2) is provided with a radial tappet oil hole (1.17) which is communicated with the tappet stepped shaft hole (1.20) and is constantly communicated with an oil hole (1.18) on the tappet sleeve;
the on-off of the oil return path (7) is controlled by the on-off state of the electromagnetic valve (8).
2. The electro-hydraulic valve timing control device according to claim 1, characterized in that: the molded line of the gas distribution cam (2) is composed of a plurality of sections of curves, and the rear section of the return combined curve is provided with a concentric circular arc which has a radius larger than the radius of the base circle of the gas distribution cam (2) and a size equal to the terminal lift value of the curve of the front section connected with the gas distribution cam.
3. The electro-hydraulic valve timing control device according to claim 1, characterized in that: the tappet sleeve (1.1), the tappet (1.2), the tappet one-way valve core spring seat (1.5) and the follow-up buffer sleeve (1.7) are coaxial; the pretightening force of the tappet spring (1.6) is greater than the sum of the pretightening force of the buffer sleeve spring (1.12) and the pretightening force of the buffer sleeve one-way valve spring (1.11), but is far less than the pretightening force of the valve spring (5.1).
4. The electro-hydraulic valve timing control device according to claim 1, characterized in that: the distance between the lower end surface of the buffer sleeve clamp spring (1.8) and the upper end surface of the tappet clamp spring (1.9) can be changed from zero to a set maximum separation distance, and the maximum separation distance is set according to the sum of the valve opening size parameter determined by the curve of the cam (2) and the maximum clearance size parameter required to be compensated by the valve driving system when the valve needs to be subjected to lag angle adjustment before being seated.
5. The electro-hydraulic valve timing control device according to claim 1, characterized in that: the follow-up buffer sleeve (1.7) is a step shaft, a step shaft hole (1.16) is arranged in the follow-up buffer sleeve, a radial hole (1.15) penetrating the step shaft hole (1.16) is arranged at the upper end of the follow-up buffer sleeve, and a throttling buffer inclined plane (1.14) is arranged on the outer circular surface of the step shaft shoulder of the follow-up buffer sleeve (1.7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921010170.2U CN210396836U (en) | 2019-07-01 | 2019-07-01 | Electro-hydraulic control device for valve timing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921010170.2U CN210396836U (en) | 2019-07-01 | 2019-07-01 | Electro-hydraulic control device for valve timing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210396836U true CN210396836U (en) | 2020-04-24 |
Family
ID=70352939
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921010170.2U Active CN210396836U (en) | 2019-07-01 | 2019-07-01 | Electro-hydraulic control device for valve timing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210396836U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110159382A (en) * | 2019-07-01 | 2019-08-23 | 贵州大学 | A kind of electro-hydraulic regulation device of valve timing |
| CN115898585A (en) * | 2022-12-10 | 2023-04-04 | 吉林大学 | Motor-driven variable-length tappet variable valve lift mechanism |
-
2019
- 2019-07-01 CN CN201921010170.2U patent/CN210396836U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110159382A (en) * | 2019-07-01 | 2019-08-23 | 贵州大学 | A kind of electro-hydraulic regulation device of valve timing |
| CN115898585A (en) * | 2022-12-10 | 2023-04-04 | 吉林大学 | Motor-driven variable-length tappet variable valve lift mechanism |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8991350B2 (en) | Reset type rocker braking method and device | |
| US6397800B2 (en) | Valve control device of internal combustion engine | |
| US5085182A (en) | Variable valve timing rocker arm arrangement for internal combustion engine | |
| CN101929365B (en) | Hydraulic self-adaption air valve correct-timing variable system of diesel engine and control method thereof | |
| CN104685169A (en) | Variable valve device for internal combustion engine | |
| CN210396836U (en) | Electro-hydraulic control device for valve timing | |
| WO2009151352A1 (en) | Late miller internal combustion engine | |
| CN209908586U (en) | Engine valve bridge structure with variable valve lift | |
| CN100419224C (en) | Valve mechanism for internal combustion engine | |
| US6672270B2 (en) | Fuel efficient valve mechanism for internal combustion engines | |
| CN108240244B (en) | Variable system of diesel engine inlet valve and diesel engine | |
| CN109653829B (en) | Electro-hydraulic control method and device for valve lag angle | |
| CN102852585B (en) | Continuous and changeable valve lift control mechanism | |
| CN210396838U (en) | Electro-hydraulic type variable valve timing adjusting device | |
| CN204827575U (en) | Valve lift adjustment mechanism and vehicle | |
| CN102278162A (en) | Variable valve lift mechanism | |
| CN212296526U (en) | Full-variable tappet cup | |
| CN110159382A (en) | A kind of electro-hydraulic regulation device of valve timing | |
| KR20080018477A (en) | Variable valve lift apparatus of engine for vehicles | |
| CN103850744A (en) | Variable valve lift mechanism | |
| CN203742695U (en) | Valve-stroke-variable mechanism | |
| CN101349177A (en) | Variable air valve apparatus of engine | |
| CN201310389Y (en) | Valve driving device of four-valve diesel engine | |
| CN107762587B (en) | Actuating mechanism, variable valve lift device, engine and automobile | |
| CN113107636B (en) | Two-section type hydraulic tappet, two-section type variable valve lift mechanism and control method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |