CN113217135B - Electric control hydraulic fully variable valve driving mechanism - Google Patents
Electric control hydraulic fully variable valve driving mechanism Download PDFInfo
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- CN113217135B CN113217135B CN202110516251.5A CN202110516251A CN113217135B CN 113217135 B CN113217135 B CN 113217135B CN 202110516251 A CN202110516251 A CN 202110516251A CN 113217135 B CN113217135 B CN 113217135B
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- valve core
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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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
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
Abstract
The invention provides an electric control hydraulic fully variable valve driving mechanism, which comprises a low-pressure valve core, a valve body, a high-pressure valve core, a cylinder sleeve and a first piston, wherein the low-pressure valve core is arranged on the low-pressure valve core; the low-pressure valve core is arranged at one side in the valve body in a sliding manner; the high-pressure valve core is arranged on the other side in the valve body in a sliding manner; a low-pressure oil cavity which can be communicated with a low-pressure oil inlet is formed in the valve body, and one end of the high-pressure valve core extends into the low-pressure oil cavity; the bottom of the valve body is provided with a pressure oil outlet; a low-pressure oil channel connected with a low-pressure oil inlet is arranged in the valve body; the other end of the low-pressure oil channel can be communicated with a pressure oil outlet; the cylinder sleeve is arranged at the bottom of the valve body, and the first piston penetrates through the cylinder sleeve; one end of the first piston can extend into the pressure oil outlet. The invention has compact structure, adopts an electric control hydraulic form to drive the valve to carry out fully variable opening and closing, reduces technical power consumption, achieves the effects of energy recovery and action buffering, and has high safety factor.
Description
Technical Field
The invention relates to the technical field of engines, in particular to an electric control hydraulic fully-variable valve driving mechanism.
Background
The variable phase and variable valve lift mechanism on the present vehicle engine is mainly a cam valve lift mechanism, which changes the distribution phase and the valve lift through the transformation of a cam, the structure can only realize the adjustment of part of the valve lift with fixed size, the opening and closing phases of the valve can not be adjusted independently, and only can realize the early opening and closing or the late opening and closing at the same time, therefore, the distribution phase and the valve lift required by the engine under different working conditions can not be adjusted reasonably;
in the working process of the existing hydraulic valve system, some systems can realize variable adjustment of valve phase and valve lift, but because the system structure is complex, the technical power consumption is large, and the oil consumption of an engine is easily influenced.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the electric control hydraulic fully-variable valve driving mechanism which is compact in structure, realizes energy recovery, has a buffering effect and is stable and reliable in driving. The technical scheme adopted by the invention is as follows:
an electrically-controlled hydraulic fully-variable valve driving mechanism comprises a hydraulic driving component and a valve control component,
the hydraulic driving assembly comprises a low-pressure valve core, a valve body and a high-pressure valve core;
the top of the valve body is provided with a low-pressure oil inlet for introducing low-pressure oil and a high-pressure oil inlet for introducing high-pressure oil; the low-pressure valve core is arranged at one side in the valve body in a sliding manner; the high-pressure valve core is arranged on the other side in the valve body in a sliding manner; a low-pressure oil cavity which can be communicated with a low-pressure oil inlet is formed in the valve body, and one end of the high-pressure valve core extends into the low-pressure oil cavity; when the low-pressure valve core moves to a certain position, low-pressure oil can enter the low-pressure oil cavity from the low-pressure oil inlet and push the high-pressure valve core to move;
the bottom of the valve body is provided with a pressure oil outlet, and when the high-pressure valve core moves to a certain position, high-pressure oil can enter the pressure oil outlet from the high-pressure oil inlet;
a low-pressure oil channel connected with a low-pressure oil inlet is arranged in the valve body; the other end of the low-pressure oil channel can be communicated with a pressure oil outlet; when the high-pressure valve core moves to a certain position, the low-pressure oil inlet and the pressure oil outlet can be communicated;
the valve control assembly comprises a cylinder sleeve and a first piston;
the cylinder sleeve is arranged at the bottom of the valve body, and the first piston penetrates through the cylinder sleeve; one end of the first piston can extend into the pressure oil outlet, and the other end of the first piston is used for being connected with the air valve.
Further, in the hydraulic drive assembly, a low-pressure valve core cavity for accommodating a low-pressure valve core is arranged on one side inside the valve body, a high-pressure valve core cavity for accommodating a high-pressure valve core is arranged on the other side inside the valve body, and one end of the high-pressure valve core cavity is communicated with the low-pressure oil cavity.
Furthermore, a reversing spring is arranged in the high-pressure valve core cavity, one end of the reversing spring is abutted against the cavity wall of the high-pressure valve core cavity, and the other end of the reversing spring is abutted against the high-pressure valve core.
Furthermore, a low-pressure oil return passage communicated with the low-pressure oil cavity is arranged at the edge of one side in the valve body, a circle of outer edge matched with the low-pressure oil return passage is arranged on the low-pressure valve core, and a low-pressure oil groove connected with the outer edge is also arranged on the peripheral surface of the low-pressure valve core; when the low-pressure valve core moves to the position where the outer edge of the low-pressure valve core contacts the outer side wall of the low-pressure oil loop channel, low-pressure oil enters the low-pressure oil cavity through the low-pressure oil inlet, the low-pressure oil groove and the low-pressure oil loop channel; when the low-pressure valve core moves to the position where the outer edge of the low-pressure valve core contacts the inner side wall of the low-pressure oil return passage, pressure relief is achieved.
Furthermore, the high-pressure valve core is provided with a high-pressure oil groove, when the high-pressure valve core reciprocates in the high-pressure valve core cavity, one end of the high-pressure oil groove can be communicated with the low-pressure oil channel or the high-pressure oil inlet, and the other end of the high-pressure oil groove is communicated with the pressure oil outlet all the time.
Furthermore, the hydraulic driving assembly further comprises an electromagnet, an armature spring and an armature, wherein one end of the armature spring is connected with the electromagnet, the other end of the armature spring is connected with one end of the low-pressure valve core, the armature is arranged at the edge of the low-pressure valve core, which is close to one side of the electromagnet, and the reciprocating motion of the low-pressure valve core in the valve body is realized through the existence of the attraction of the armature caused by the on-off electricity of the electromagnet.
Further, in the valve control assembly, the valve control assembly further comprises a second piston, a cylinder sleeve hydraulic cavity corresponding to the pressure oil outlet is formed in the top of the cylinder sleeve, the second piston is arranged in the cylinder sleeve hydraulic cavity and sleeved on the first piston, a gap exists between the first piston and the second piston, and a gap exists between the outer peripheral surface of the top of the first piston and the pressure oil outlet, so that the pressure oil can smoothly enter the cylinder sleeve hydraulic cavity.
Furthermore, a hydraulic loop communicated with a cylinder sleeve hydraulic cavity is arranged in the cylinder sleeve, a recovery channel is arranged at the bottom of the valve body, one end of the recovery channel is communicated with the hydraulic loop, and the other end of the recovery channel is communicated with the low-pressure oil cavity.
Furthermore, a first step for limiting the motion stroke of the second piston is arranged at the upper part in the cylinder sleeve hydraulic cavity, and a second step for limiting the motion stroke of the first piston is arranged at the middle part in the cylinder sleeve hydraulic cavity.
Furthermore, an upper step matched with the second piston is arranged in the middle of the first piston, and when the first piston moves upwards to enable the upper step to abut against the second piston, the first piston can drive the second piston to synchronously move upwards;
the middle part of the first piston is positioned at the lower side of the upper step and is provided with a lower step;
and a middle oil cavity is arranged in the middle of the top of the first piston, and a transverse through hole communicated with the middle oil cavity is arranged at the middle part of the first piston, is positioned at the lower side of the lower step and penetrates through the middle part of the first piston.
The invention has the advantages that:
the hydraulic drive assembly and the valve control assembly are combined to realize hydraulic path conversion, and the lifting of the valve can be realized only by two external structures, namely the valve body and the cylinder sleeve, so that the structure is simplified, the arrangement is more convenient, the lifting of the valve is continuously adjusted by setting the switching of two internal high-pressure and low-pressure oil paths, and the opening size of the valve lift is changed by controlling the pressure of high-pressure oil;
in the process of opening the valve, in the process that the first piston continues to move under inertia after being stressed in a balanced manner, high-pressure oil is continuously supplemented into the hydraulic cavity of the cylinder sleeve, so that the opening stability of the valve is ensured, energy conversion is realized, and kinetic energy recovery is facilitated;
in the opening or closing process of the valve, high-pressure oil in the hydraulic cavity of the cylinder sleeve can flow to the low-pressure oil cavity through the recovery channel or the low-pressure oil channel, so that the high-pressure oil can be recycled;
by utilizing the matching of the second step in the hydraulic cavity of the cylinder sleeve and the lower step on the first piston, when pressure oil in a space between the second step and the lower step is compressed, hydraulic buffering in the descending process of the first piston is realized, and the rigid collision of parts is avoided;
in the valve closing process, when the top of the first piston enters the pressure oil outlet, the gap between the first piston and the second piston enables the inner of the cylinder sleeve hydraulic cavity to form a throttling effect, the pressure in the cylinder sleeve hydraulic cavity is increased, the first piston and the second piston are buffered, the rigid collision of parts is avoided, meanwhile, high-pressure oil flows back to the low-pressure oil way, and a low-pressure source during the next circulation can be filled.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a schematic structural diagram of the hydraulic drive assembly of the present invention.
FIG. 3 is a state diagram of the hydraulic drive assembly and the valve control assembly when the valve of the present invention is open.
FIG. 4 is a state diagram of the hydraulic drive assembly and the valve control assembly during valve closing cushion of the present invention.
Fig. 5 is a schematic structural view of the low-pressure oil passage of the present invention.
Fig. 6 is a schematic structural view of the high-pressure oil passage of the present invention.
In the figure: 1-a hydraulic drive assembly, 2-a valve control assembly, 3-a low pressure oil circuit, 4-a high pressure oil circuit, 5-a valve, 6-a valve seat, 7-a valve spring, 101-an electromagnet, 102-an armature spring, 103-an armature, 104-a low pressure spool, 105-a valve body, 106-a reversing spring, 107-a high pressure spool, 1041-a low pressure oil sump, 1051-a low pressure oil inlet, 1052-a low pressure spool cavity, 1053-a low pressure oil channel, 1054-a high pressure oil inlet, 1055-a high pressure spool cavity, 1056-a pressure oil outlet, 1057-a low pressure oil cavity, 1058-a recovery channel, 1059-a low pressure oil return channel, 1071-a high pressure oil sump, 201-a cylinder liner, 202-a first piston, 203-a second piston, 2011-a cylinder liner hydraulic cavity, 2012-first step, 2013-hydraulic circuit, 2014-second step, 2021-upper step, 2022-middle oil chamber, 2023-lower step, 2024-transverse through hole, 301-low pressure source, 302-low pressure oil rail, 303-low pressure limiting valve, 401-high pressure source, 402-high pressure oil rail, 403-high pressure limiting valve, 404-check valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Referring to fig. 1, the present invention provides an electrically controlled hydraulic fully variable valve actuating mechanism, which includes a hydraulic actuating assembly 1, a valve control assembly 2, a low pressure oil path 3, a high pressure oil path 4, a valve 5, a valve spring 6, and a valve seat 7.
Referring to fig. 2, the hydraulic drive assembly 1 includes an electromagnet 101, an armature spring 102, an armature 103, a low pressure spool 104, a valve body 105, and a high pressure spool 107;
one end of an armature spring 102 is connected with the electromagnet 101, the other end of the armature spring is connected with one end of a low-pressure valve core 104, the armature 103 is arranged at the edge of one side, close to the electromagnet 101, of the low-pressure valve core 104, the attraction force of the armature 103 is generated or not through the on-off of the electromagnet 101, the reciprocating motion of the low-pressure valve core 104 in the valve body 1 is realized, and then the opening and closing phase of the valve is continuously adjusted.
The top of the valve body 105 is provided with a low-pressure oil inlet 1051 for introducing low-pressure oil and a high-pressure oil inlet 1054 for introducing high-pressure oil; the low pressure spool 104 is slidably disposed on one side in the valve body 105; the high-pressure valve core 107 is arranged at the other side in the valve body 105 in a sliding way; a low-pressure oil chamber 1057 that can communicate with the low-pressure oil inlet 1051 is provided in the valve body 105, and one end of the high-pressure spool 107 extends into the low-pressure oil chamber 1057.
The bottom of the valve body 105 is provided with a pressure oil outlet 1056, and when the high pressure spool 107 moves to a certain position, high pressure oil can enter the pressure oil outlet 1056 from the high pressure oil inlet 1054.
A low-pressure oil passage 1053 connected to the low-pressure oil inlet 1051 is provided in the valve body 105; the other end of the low-pressure oil passage 1053 can communicate with a pressure oil outlet 1056; when the high pressure spool 107 moves to a certain position, the low pressure oil inlet 1053 and the pressure oil outlet 1056 can be conducted.
Specifically, a low-pressure spool cavity 1052 for accommodating the low-pressure spool 104 is arranged on one side inside the valve body 105, a high-pressure spool cavity 1055 for accommodating the high-pressure spool 107 is arranged on the other side inside the valve body 105, and one end of the high-pressure spool cavity 1055 is communicated with the low-pressure oil cavity 1057; when the low-pressure valve core 104 moves to a certain position, low-pressure oil can enter the low-pressure oil cavity 1057 from the low-pressure oil inlet 1051 and push the high-pressure valve core 107 to move;
a low-pressure oil loop channel 1059 communicated with the low-pressure oil cavity 1057 is arranged at the edge of one side in the valve body 105, a circle of outer edge matched with the low-pressure oil loop channel 1059 is arranged on the low-pressure valve core 104, and a low-pressure oil groove 1041 connected with the outer edge is also arranged on the circumferential surface of the low-pressure valve core 104; when the low-pressure spool 104 moves to the position where the outer edge of the low-pressure spool contacts the outer side wall of the low-pressure oil return passage 1059, low-pressure oil enters the low-pressure oil chamber 1057 through the low-pressure oil inlet 1051, the low-pressure oil groove 1041 and the low-pressure oil return passage 1059; when the low-pressure valve core 104 moves to the position that the outer edge of the low-pressure valve core contacts the inner side wall of the low-pressure oil return channel 1059, pressure relief is realized;
a high-pressure oil groove 1071 is arranged on the high-pressure valve core 107, when the high-pressure valve core 107 reciprocates in the high-pressure valve core cavity 1055, one end of the high-pressure oil groove 1071 can be communicated with the low-pressure oil channel 1053 or the high-pressure oil inlet 1054, and the other end is communicated with the pressure oil outlet 1056 all the time; by switching the communication paths of the high-pressure oil groove 1071 with the low-pressure oil passage 1053 and the high-pressure oil inlet 1054, the flow of the low-pressure oil or the high-pressure oil is switched.
A reversing spring 106 is also arranged in the high-pressure valve core cavity 1055, one end of the reversing spring 106 is abutted against the cavity wall of the high-pressure valve core cavity 1055, and the other end thereof is abutted against the high-pressure valve core 107; the reset function of the high-pressure valve core 107 is achieved through the elasticity of the reversing spring 106, and repeated use is achieved.
In practice, when the electromagnet 101 is energized, the armature 103 drives the low-pressure valve spool 104 to approach the electromagnet 101, the armature spring 102 compresses, the low-pressure oil inlet 1051 and the low-pressure oil chamber 1057 are communicated, the low-pressure oil enters the low-pressure oil chamber 1057 through the low-pressure oil inlet 1051, the low-pressure oil groove 1041 and the low-pressure oil loop channel 1059, the high-pressure valve spool 107 is pushed to slide in the high-pressure valve spool chamber 1055, the reversing spring 106 compresses, the high-pressure oil inlet 1054 and the pressure oil outlet 1056 are communicated, and the high-pressure oil enters the pressure oil outlet 1056 through the high-pressure oil inlet 1054 and the high-pressure oil groove 1071 and is used for driving the valve to open;
when the electromagnet 101 is powered off, the armature 103 drives the low-pressure valve spool 104 to return quickly under the action of the armature spring 102, the low-pressure oil in the low-pressure oil chamber 1057 is released quickly through the low-pressure oil circuit channel 1059, and the high-pressure valve spool 107 is reset quickly under the action of the reversing spring 106, so that the low-pressure oil channel 1053 and the high-pressure oil tank 1071 are communicated for closing the valve.
Referring to fig. 3-4, the valve control assembly 2 includes a cylinder 201, a first piston 202, and a second piston 203; the cylinder liner 201 is arranged at the bottom of the valve body 105, and the first piston 202 penetrates through the cylinder liner 201; one end of the first piston 202 can extend into the pressure oil outlet 1056, and the other end is used for connecting the air valve 5; the other end of the valve 5 penetrates through a valve seat 7, and a valve spring 6 is provided between the valve seat 7 and the valve 5, and a restoring force is provided to the valve 5 by deformation of the valve spring 6.
Specifically, a cylinder sleeve hydraulic cavity 2011 corresponding to the pressure oil outlet 1056 is arranged at the top of the cylinder sleeve 201, the second piston 203 is arranged in the cylinder sleeve hydraulic cavity 2011 and sleeved on the first piston 202, a gap exists between the first piston 202 and the second piston 203, and a gap exists between the outer peripheral surface of the top of the first piston 202 and the pressure oil outlet 1056, so that pressure oil can smoothly enter the cylinder sleeve hydraulic cavity 2011;
as an embodiment of the present application, the top cross-sectional shape of the first piston 202 is a conical surface, when the valve 5 is returned to make the first piston 202 and the second piston 203 go upward, the top of the first piston 202 enters the pressure oil outlet 1056, the oil path between the top of the first piston 202 and the pressure oil outlet 1056 is instantly narrowed, the back clearance is decreased from large to small, the oil pressure in the cylinder liner hydraulic chamber 2011 is instantly increased when the oil path is suddenly narrowed, the pressure between the top of the second piston 203 and the top of the cylinder liner hydraulic chamber 2011 is instantly increased, a buffer effect is performed on the first piston 202 and the second piston 203, at this time, high-pressure oil is recovered through the cylinder liner hydraulic chamber 2011, the pressure oil outlet 1056, the low-pressure oil passage 1053 and the low-pressure oil inlet 1051, and is used as low-pressure oil for the next cycle, which is beneficial to improving the utilization rate.
A hydraulic circuit 2013 communicated with a cylinder sleeve hydraulic cavity 2011 is arranged in the cylinder sleeve 201, a recovery channel 1058 is arranged at the bottom of the valve body 105, one end of the recovery channel 1058 is communicated with the hydraulic circuit 2013, and the other end of the recovery channel 1058 is communicated with a low-pressure oil cavity 1057; when the first piston 202 moves downwards to open the valve 5, the high-pressure oil in the cylinder sleeve hydraulic cavity 2011 flows into the low-pressure oil cavity 1057 through the hydraulic circuit 2013 and the recovery channel 1058, and the high-pressure oil is recycled.
A first step 2012 for limiting the movement stroke of the second piston 203 is arranged at the upper part in the cylinder sleeve hydraulic cavity 2011, and a second step 2014 for limiting the movement stroke of the first piston 202 is arranged at the middle part in the cylinder sleeve hydraulic cavity 2011; specifically, the first step 2012 is located at the lower side of the lowest end of the hydraulic circuit 2013, and ensures that the pressure oil left when the first piston 202 is buffered has sufficient pressure.
An upper step 2021 matched with the second piston 203 is arranged in the middle of the first piston 202, and when the first piston 202 moves upwards until the upper step 2021 abuts against the second piston 203, the first piston 202 can drive the second piston 203 to move upwards synchronously;
the middle part of the first piston 202 is positioned at the lower side of the upper step 2021 and is provided with a lower step 2023;
an intermediate oil chamber 2022 is arranged in the middle of the top of the first piston 202, and a transverse through hole 2024 communicated with the intermediate oil chamber 2022 penetrates through the middle part of the first piston and is positioned below the lower step 2023; the middle oil cavity 2022 and the transverse through hole 2024 realize that high-pressure oil smoothly enters between the lower step 2023 and the second step 2014; when the high-pressure oil has a large pressure and the first piston 202 descends to the lower side of the second step 2014 of the transverse through hole 2024, the high-pressure oil between the second step 2014 and the lower step 2023 is compressed to generate a large hydraulic pressure to slow down the first piston 202 to descend continuously, so that the first piston 202 is prevented from being damaged due to collision between the first piston 202 and the end surface of the cylinder sleeve 201.
Referring to fig. 5, the low-pressure oil path 3 includes a low-pressure source 301, a low-pressure oil rail 302 and a low-pressure limiting valve 303; .
In the low-pressure oil path 3, one end of the low-pressure source 301 is connected to the oil tank, the other end is connected to the low-pressure oil rail 302, one end of the low-pressure limiting valve 303 is connected to the oil tank, the other end is connected to the low-pressure oil rail 302, and the output end of the low-pressure oil rail 302 is communicated with a low-pressure oil inlet 1051 on the valve body 105 and used for outputting low-pressure oil.
Referring to fig. 6, the high-pressure oil path 4 includes a high-pressure source 401, a high-pressure oil rail 402 and a high-pressure limiting valve 403;
in the high-pressure oil path 4, one end of a high-pressure source 401 is connected with an oil tank, the other end of the high-pressure source is connected with a high-pressure oil rail 402, one end of a high-pressure limiting valve 403 is connected with the oil tank, the other end of the high-pressure limiting valve 403 is connected with the high-pressure oil rail 402, and the other end of the high-pressure oil rail 402 is communicated with a high-pressure oil inlet 1054 on the valve body 105 and used for outputting high-pressure oil; the oil pressure of the high-pressure oil is controlled by controlling the pressure in the high-pressure oil rail 402, and then the opening of the valve lift is controlled.
Specifically, a check valve 404 is arranged between the output end of the high-pressure oil rail 402 and the high-pressure oil inlet 1054, and in the descending process of the first piston 202, the high-pressure oil in the high-pressure oil path 4 is timely supplemented into the cylinder sleeve hydraulic cavity 2011, and the check valve 404 can prevent the backflow of the high-pressure oil, so that the valve lift is ensured to be stably opened, the kinetic energy conversion is facilitated, and the kinetic energy recovery is realized.
As an embodiment of the application, cold starting auxiliary heating devices are respectively arranged in the low-pressure oil path 3 and the high-pressure oil path 4, so that the problem that the whole mechanism is difficult to start under the low-temperature condition is solved.
The working principle is as follows:
the electromagnet 101 is electrified, the low-pressure valve core 104 is close to the electromagnet 101, the outer edge of the low-pressure valve core 104 is abutted to the outer side wall of the low-pressure oil loop channel 1059, the low-pressure oil way 3 is opened, low-pressure oil enters the low-pressure oil cavity 1057 through the low-pressure oil inlet 1051, the low-pressure oil groove 1041 and the lower side of the low-pressure oil loop channel 1059, the high-pressure valve core 107 compresses the reversing spring 106 under the action of hydraulic pressure until the high-pressure oil groove 1071 conducts the high-pressure oil inlet 1054 and the pressure oil outlet 1056, the high-pressure oil way 4 is opened, and the high-pressure oil smoothly enters the cylinder sleeve hydraulic cavity 2011 through the pressure oil outlet 1056;
the hydraulic pressure in the cylinder sleeve hydraulic cavity 2011 is increased to push the first piston 202 and the second piston 203 to move downwards, when the first piston 202 overcomes the elastic force of the valve spring 6 to move downwards, the valve 5 is opened, because different high-pressure oil pressures correspond to corresponding valve lifts, when the first piston 202 is stressed to be balanced, the first piston 202 can continue to move downwards under the action of inertia to overcome the larger elastic force of the valve spring 6 to perform deceleration movement until the first piston stops moving, at the moment, the high-pressure oil in the high-pressure oil way 4 can be timely supplemented into the cylinder sleeve hydraulic cavity 2011, and the check valve 404 prevents the backflow of the high-pressure oil, so that the valve lifts are ensured to be stably opened, the kinetic energy conversion is facilitated, and the kinetic energy recovery is realized;
when the valve 5 is closed, the electromagnet 101 is powered off, the armature spring 102, the armature 103 and the low-pressure valve core 104 are reset, the outer edge of the low-pressure valve core 104 is abutted to the inner side wall of the low-pressure oil loop channel 1059, low-pressure oil is discharged from the low-pressure oil cavity 1057 to the low-pressure oil loop channel 1059, the high-pressure valve core 107 is reset under the action of the reversing spring 106, the high-pressure oil groove 1071 conducts the low-pressure oil channel 1053 and the cylinder sleeve hydraulic cavity 2011, the high-pressure oil way 4 is closed, the hydraulic pressure in the cylinder sleeve hydraulic cavity 2011 is instantly reduced, the first piston 202 is stressed to lose balance and moves upwards under the action of the valve spring 6, the valve 5 is driven to move upwards, and the high-pressure oil is recovered through the cylinder sleeve hydraulic cavity 2011, the pressure oil outlet 1056, the low-pressure oil channel 1053 and the low-pressure oil inlet 1051 to serve as low-pressure oil for next circulation until the valve 5 is closed.
Finally, it should be noted that the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, and although the present invention has been described in detail with reference to examples, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered by the claims of the present invention.
Claims (10)
1. The utility model provides an automatically controlled hydraulic pressure is variable valve actuating mechanism entirely, includes hydraulic drive subassembly (1) and valve control assembly (2), its characterized in that:
the hydraulic drive assembly (1) comprises a low-pressure valve core (104), a valve body (105) and a high-pressure valve core (107);
the top of the valve body (105) is provided with a low-pressure oil inlet (1051) for introducing low-pressure oil and a high-pressure oil inlet (1054) for introducing high-pressure oil; the low-pressure valve core (104) is arranged at one side in the valve body (105) in a sliding way; the high-pressure valve core (107) is arranged at the other side in the valve body (105) in a sliding way; a low-pressure oil cavity (1057) which can be communicated with a low-pressure oil inlet (1051) is arranged in the valve body (105), and one end of the high-pressure valve core (107) extends into the low-pressure oil cavity (1057); when the low-pressure valve core (104) moves to a certain position, low-pressure oil can enter the low-pressure oil cavity (1057) from the low-pressure oil inlet (1051) and push the high-pressure valve core (107) to move;
the bottom of the valve body (105) is provided with a pressure oil outlet (1056), and when the high-pressure valve core (107) moves to a certain position, high-pressure oil can enter the pressure oil outlet (1056) from the high-pressure oil inlet (1054);
a low-pressure oil channel (1053) connected with a low-pressure oil inlet (1051) is arranged in the valve body (105); the other end of the low-pressure oil channel (1053) can be communicated with a pressure oil outlet (1056); when the high-pressure valve core (107) moves to a certain position, the low-pressure oil inlet (1053) and the pressure oil outlet (1056) can be communicated;
the valve control assembly (2) comprises a cylinder sleeve (201) and a first piston (202);
the cylinder sleeve (201) is arranged at the bottom of the valve body (105), and the first piston (202) penetrates through the cylinder sleeve (201); one end of the first piston (202) can extend into the pressure oil outlet (1056), and the other end of the first piston is connected with the air valve (5).
2. The electrically controlled hydraulic fully variable valve driving mechanism according to claim 1, characterized in that: in the hydraulic drive assembly (1), a low-pressure valve core cavity (1052) for accommodating a low-pressure valve core (104) is arranged on one side in the valve body (105), a high-pressure valve core cavity (1055) for accommodating a high-pressure valve core (107) is arranged on the other side in the valve body (105), and one end of the high-pressure valve core cavity (1055) is communicated with a low-pressure oil cavity (1057).
3. The electrically controlled hydraulic fully variable valve driving mechanism according to claim 2, characterized in that: and a reversing spring (106) is also arranged in the high-pressure valve core cavity (1055), one end of the reversing spring (106) is abutted against the cavity wall of the high-pressure valve core cavity (1055), and the other end of the reversing spring is abutted against the high-pressure valve core (107).
4. The electrically controlled hydraulic fully variable valve driving mechanism according to any one of claims 2 or 3, characterized in that: a low-pressure oil return channel (1059) communicated with a low-pressure oil cavity (1057) is arranged at the edge of one side in the valve body (105), a circle of outer edge matched with the low-pressure oil return channel (1059) is arranged on the low-pressure valve core (104), and a low-pressure oil groove (1041) connected with the outer edge is also arranged on the circumferential surface of the low-pressure valve core (104); when the low-pressure valve core (104) moves to the outer edge to contact the outer side wall of the low-pressure oil return passage (1059), low-pressure oil enters the low-pressure oil cavity (1057) through the low-pressure oil inlet (1051), the low-pressure oil groove (1041) and the low-pressure oil return passage (1059), and when the low-pressure valve core (104) moves to the outer edge to contact the inner side wall of the low-pressure oil return passage (1059), pressure relief is realized.
5. The electrically controlled hydraulic fully variable valve driving mechanism according to any one of claims 2 or 3, characterized in that: the high-pressure spool (107) is provided with a high-pressure oil groove (1071), when the high-pressure spool (107) reciprocates in the high-pressure spool cavity (1055), one end of the high-pressure oil groove (1071) can be communicated with the low-pressure oil channel (1053) or the high-pressure oil inlet (1054), and the other end of the high-pressure oil groove is communicated with the pressure oil outlet (1056) all the time.
6. The electrically controlled hydraulic fully variable valve driving mechanism according to any one of claims 1 to 3, characterized in that: in the hydraulic drive assembly (1), the hydraulic drive assembly further comprises an electromagnet (101), an armature spring (102) and an armature (103), one end of the armature spring (102) is connected with the electromagnet (101), the other end of the armature spring is connected with one end of a low-pressure valve core (104), the armature (103) is arranged at the edge of one side, close to the electromagnet (101), of the low-pressure valve core (104), and the reciprocating motion of the low-pressure valve core (104) in the valve body (1) is realized through the fact that the electromagnet (101) is switched on or off to attract the armature (103).
7. The electrically controlled hydraulic fully variable valve driving mechanism according to claim 1, characterized in that: in valve control assembly (2), still include second piston (203), cylinder liner hydraulic pressure chamber (2011) corresponding with pressure oil export (1056) is established at cylinder liner (201) top, second piston (203) are located in cylinder liner hydraulic pressure chamber (2011) and are overlapped on first piston (202), there is the clearance between first piston (202) and second piston (203), there is the clearance between first piston (202) top peripheral face and pressure oil export (1056) to make pressure oil can get into smoothly in cylinder liner hydraulic pressure chamber (2011).
8. The electrically controlled hydraulic fully variable valve driving mechanism according to claim 7, characterized in that: a hydraulic loop (2013) communicated with a cylinder sleeve hydraulic cavity (2011) is arranged in the cylinder sleeve (201), a recovery channel (1058) is arranged at the bottom of the valve body (105), one end of the recovery channel (1058) is communicated with the hydraulic loop (2013), and the other end of the recovery channel is communicated with a low-pressure oil cavity (1057).
9. The electrically controlled hydraulic fully variable valve driving mechanism according to claim 7, characterized in that: and a first step (2012) for limiting the movement stroke of the second piston (203) is arranged at the upper part in the cylinder sleeve hydraulic cavity (2011), and a second step (2014) for limiting the movement stroke of the first piston (202) is arranged at the middle part in the cylinder sleeve hydraulic cavity (2011).
10. The electrically controlled hydraulic fully variable valve driving mechanism according to any one of claims 7 to 9, characterized in that:
an upper step (2021) matched with the second piston (203) is arranged in the middle of the first piston (202), and when the first piston (202) moves upwards to the upper step (2021) and abuts against the second piston (203), the first piston (202) can drive the second piston (203) to synchronously move upwards;
a lower step (2023) is arranged at the lower side of the upper step (2021) in the middle of the first piston (202);
an intermediate oil chamber (2022) is arranged in the middle of the top of the first piston (202), and a transverse through hole (2024) communicated with the intermediate oil chamber (2022) penetrates through the middle of the lower step (2023).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110516251.5A CN113217135B (en) | 2021-05-12 | 2021-05-12 | Electric control hydraulic fully variable valve driving mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110516251.5A CN113217135B (en) | 2021-05-12 | 2021-05-12 | Electric control hydraulic fully variable valve driving mechanism |
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| CN113217135A CN113217135A (en) | 2021-08-06 |
| CN113217135B true CN113217135B (en) | 2022-02-08 |
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| CN115142927B (en) * | 2022-07-28 | 2023-09-08 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic full-variable valve driving mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0139566A1 (en) * | 1983-09-23 | 1985-05-02 | Societe Alsacienne De Constructions Mecaniques De Mulhouse | Electro-hydraulic unit for the control of the valves of an internal-combustion engine |
| US6966285B1 (en) * | 2004-07-21 | 2005-11-22 | General Motors Corporation | Engine valve actuation control and method |
| CN104641080A (en) * | 2012-07-06 | 2015-05-20 | 弗瑞瓦勒夫股份公司 | Actuator for axial displacement of a gas exchange valve in a combustion engine |
| CN107676142A (en) * | 2017-11-13 | 2018-02-09 | 吉林大学 | A kind of hydraulic-driven variable valve actuator for air of low voltage control high pressure |
| CN211474201U (en) * | 2019-11-07 | 2020-09-11 | 一汽解放汽车有限公司 | Fully variable valve system of engine |
-
2021
- 2021-05-12 CN CN202110516251.5A patent/CN113217135B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0139566A1 (en) * | 1983-09-23 | 1985-05-02 | Societe Alsacienne De Constructions Mecaniques De Mulhouse | Electro-hydraulic unit for the control of the valves of an internal-combustion engine |
| US6966285B1 (en) * | 2004-07-21 | 2005-11-22 | General Motors Corporation | Engine valve actuation control and method |
| CN104641080A (en) * | 2012-07-06 | 2015-05-20 | 弗瑞瓦勒夫股份公司 | Actuator for axial displacement of a gas exchange valve in a combustion engine |
| CN107676142A (en) * | 2017-11-13 | 2018-02-09 | 吉林大学 | A kind of hydraulic-driven variable valve actuator for air of low voltage control high pressure |
| CN211474201U (en) * | 2019-11-07 | 2020-09-11 | 一汽解放汽车有限公司 | Fully variable valve system of engine |
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