CN109630229B - High-compact rocker arm switching device of engine - Google Patents
High-compact rocker arm switching device of engine Download PDFInfo
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- CN109630229B CN109630229B CN201811279704.1A CN201811279704A CN109630229B CN 109630229 B CN109630229 B CN 109630229B CN 201811279704 A CN201811279704 A CN 201811279704A CN 109630229 B CN109630229 B CN 109630229B
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- rocker arm
- movable
- valve
- movable rocker
- cam
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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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
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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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
Abstract
The invention discloses a high-compact rocker arm switching device of an engine, which comprises a cam, a tappet, a rocker arm mechanism and a valve assembly, wherein the cam is arranged on the tappet; a first molded line and a second molded line are arranged on the outer surface of the cam; the rocker arm mechanism comprises a rocker arm body, a first movable rocker arm capable of being matched with the first molded line and a second movable rocker arm capable of being matched with the second molded line, a hydraulic actuating mechanism capable of being matched with the upper end part and the lower end part of the two movable rocker arms is arranged in the rocker arm body, the rocker arms can be switched by controlling the hydraulic actuating mechanism, the matching rule between the movable rocker arms and the molded lines of the cam is changed, and two-four-stroke variable is achieved. The invention only needs one hydraulic actuating mechanism, does not need to operate the control mechanism under each working cycle, and can be adjusted under the working condition that the stroke needs to be changed, the structure and the control are simple, and the invention is beneficial to the engineering application of the variable valve technology.
Description
Technical Field
The invention belongs to the technical field of variable valves of engines, and particularly relates to a high-compactness rocker arm switching device of an engine.
Background
Internal combustion engines are still the prime mover with the highest thermal efficiency and the largest power per unit volume and weight, and have wide application, however, with the gradual shortage of world energy and the continuous deterioration of environmental resources, the internal combustion engines are required to meet more strict emission regulations and economic indexes. The traditional internal combustion engine adopts a camshaft with a fixed molded line to drive a valve, so that the emission and the oil consumption of the internal combustion engine cannot be optimal at all working conditions, and therefore, most of novel internal combustion engines adopt a variable valve technology to control the emission and reduce the oil consumption.
The variable valve technology is mainly divided into a variable valve distribution technology based on a camshaft and a cam-free valve distribution technology at present. The former mainly changes the mechanical structure, so the structure is simple, the response speed is fast, but because the cam is kept, the valve is only relatively variable, and can not be arbitrarily variable. The valve timing, lift and duration can be changed at will by the cam-free valve distribution technology. The driving mode is divided into two modes, namely electromagnetic driving, electric driving, motor driving, electro-hydraulic driving and the like. Compared with the defects of high energy consumption of electromagnetic drive, low and unstable response speed of electric drive, complex system of motor drive and the like, the electro-hydraulic drive cam-free gas distribution technology has the advantages of relatively simple structure and relatively high response speed. However, it also has unavoidable disadvantages: the flow of the hydraulic system is insufficient at high rotating speed, the valve reaches the maximum lift and the seating position quickly, and the impact force is large. Therefore, the valve stroke control device is mainly used for engines with low rotating speed such as diesel engines, and besides, expensive electro-hydraulic servo systems and relatively complex control technologies are required to accurately control the valve stroke to avoid seating impact, so that the cost of the engine is greatly increased. Accordingly, it is desirable to employ suitable variable valve technology for specific engine applications.
The variable valve mechanism in the prior art is large in size, not beneficial to compact arrangement, and needs to be improved innovatively to realize efficient and high-compact rocker arm switching work.
Disclosure of Invention
In view of this, the present invention is directed to a high-compactness rocker arm switching device for an engine, which can realize two-four stroke interchange function by changing the matching relationship between two cam profiles and a rocker arm.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a high-compactness rocker arm switching device of an engine comprises a cam, a tappet, a rocker arm mechanism and a valve assembly;
a first molded line and a second molded line are arranged on the outer surface of the cam;
the rocker arm mechanism comprises a rocker arm body, a first movable rocker arm and a second movable rocker arm, wherein the first movable rocker arm and the second movable rocker arm are respectively positioned on two sides of the rocker arm body; one end of the first movable rocker arm and one end of the second movable rocker arm are both hinged with the rocker arm body through rocker arms;
the first movable rocker arm can be in contact fit with the first molded line; the second movable rocker arm can be in contact fit with the second molded line;
a hydraulic actuating mechanism is arranged in the rocker arm body, and mutual switching between the matching of the first movable rocker arm and the first molded line and the matching of the second movable rocker arm and the second molded line is realized by controlling the hydraulic actuating mechanism;
the valve assembly comprises a valve, a valve spring and a valve seat;
one end of the bottom of the rocker arm body is matched with the top of the valve.
Further, a first oil duct and a second oil duct are arranged inside the tappet; the hydraulic actuating mechanism comprises a piston, a third oil duct and a fourth oil duct;
a first piston rod and a second piston rod are arranged on one side, close to the valve assembly, of the piston; the first movable rocker arm is matched with the first piston rod; the second movable rocker arm is matched with the second piston rod.
The other end of the bottom of the rocker arm body is provided with a half-moon groove which is matched with the top of the tappet; the first oil duct is communicated with the third oil duct through the crescent moon groove, and the second oil duct is communicated with the fourth oil duct through the crescent moon groove;
the third oil duct and the fourth oil duct are externally connected with a three-position four-way electromagnetic valve.
Furthermore, a first chute and a first locking groove are respectively arranged at the upper end and the lower end of the first movable rocker arm; the first inclined groove and the first locking groove can be matched with the first piston rod respectively;
the upper end and the lower end of the second movable rocker arm are respectively provided with a second chute and a second locking groove; the second inclined groove and the second locking groove can be respectively matched with the second piston rod.
Furthermore, bosses are arranged on two sides of the bottom of the rocker arm body; springs are arranged between the boss and the bottoms of the first movable rocker arm and the second movable rocker arm.
Furthermore, one end of the bottom of the rocker arm body is provided with a groove which is matched with the top of the valve.
Further, the first profile has two symmetrical convex ends, and the second profile has one convex end; the wrap angle and the protrusion height of any protrusion end in the first molded line are smaller than those of the second molded line.
Further, the cam rotating speed is half of the engine rotating speed.
Compared with the prior art, the high-compactness rocker arm switching device for the engine has the following advantages:
according to the high-compactness rocker arm switching device for the engine, the position of the piston in the hydraulic actuating mechanism is timely controlled, the matching rule between the piston rod and the movable rocker arm is changed, the rocker arm can be switched, and two-stroke and four-stroke change is realized. The invention only needs one hydraulic actuating mechanism, does not need to operate the control mechanism under each working cycle, but can be adjusted under the working condition that the stroke needs to be changed, the structure and the control are simple, and when one movable rocker arm is matched with the cam, the other movable rocker arm is not in contact with the cam, the abrasion is reduced, and the invention is beneficial to the engineering application of the variable valve technology.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a front view of a valve closed in a two-stroke mode of an embodiment of the present invention (about to cam a first profile 101 and a second profile 102);
FIG. 2 is a top view of the cam of FIG. 1;
FIG. 3 is a front view of the tappet of FIG. 1;
FIG. 4 is a front view of the valve mechanism of FIG. 1;
FIG. 5 is a front view of the rocker mechanism of FIG. 1;
FIG. 6 is a rear view of FIG. 5;
FIG. 7 is a top view of FIG. 5;
FIG. 8 is a left side view of the piston of FIG. 5;
FIG. 9 is a front view of the embodiment of the present invention in a two-stroke mode with the valve open;
FIG. 10 is a rear view of FIG. 9;
FIG. 11 is a front view of the valve closing position in the two-stroke mode of the present invention (the starting point of the two-stroke to four-stroke transition, i.e., the first profile 101 is about to bulge and the second profile 102 is in the base circle);
FIG. 12 is a front view of the valve closing during the switching from the two-stroke mode to the four-stroke mode according to the embodiment of the present invention (the first profile 101 is convex, and the second profile 102 is in the base circle state);
FIG. 13 is a front view of the valve closing in the four-stroke mode of the present invention (first profile 101 raised and second profile 102 in base circle);
FIG. 14 is a front view of the embodiment of the present invention in a four stroke mode with the valve open;
FIG. 15 is a front view of the valve closed in the four-stroke mode of the present invention (the starting point of the four-stroke to two-stroke transition, i.e., the first profile 101 and the second profile 102 are about to bulge);
FIG. 16 is a front view of the valve closed in the four-stroke to two-stroke mode of the present invention (the second profile 102 is convex before the first profile 101);
fig. 17 is a rear view of fig. 16.
Description of reference numerals:
1. the camshaft comprises a cam, 2, a tappet, 3, a rocker arm mechanism, 4, a valve assembly, 101, a first molded line, 102, a second molded line 201, a first oil channel, 202, a second oil channel, 301, a rocker arm body, 302, a boss, 303, a groove, 304, a spring, 305, a rocker shaft, 306, a first movable rocker arm, 307, a first locking groove, 308, a first inclined groove, 309, a hydraulic actuator, 310, a piston, 311, a third oil channel, 312, a half-moon groove, 313, a fourth oil channel, 314, a second movable rocker arm, 315, a second inclined groove, 316, a second locking groove, 317, a first piston rod, 318, a second piston rod, 401, a valve, 402, a valve spring and 403, and a valve seat.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
As shown in fig. 1 to 11, the present invention includes a cam 1, a tappet 2, a rocker mechanism 3, and a valve assembly 4; a first molded line 101 and a second molded line 102 are arranged on the outer surface of the cam 1; a first oil passage 201 and a second oil passage 202 are arranged in the tappet 2; the rocker arm mechanism 3 comprises a rocker arm body 301, and a first movable rocker arm 306 and a second movable rocker arm 314 which are respectively positioned at two sides of the rocker arm body 301; the valve assembly 4 comprises a valve 401, a valve spring 402 and a valve seat 403;
a hydraulic actuator 309 is arranged inside the rocker arm body 301, and the hydraulic actuator 309 comprises a piston 310, a third oil channel 311 and a fourth oil channel 313; a first piston rod 317 and a second piston rod 318 are arranged on one side of the piston 310 close to the valve assembly 4;
one end of the first movable rocker arm 306 and one end of the second movable rocker arm 314 are both hinged with the rocker arm body 301 through a rocker arm shaft 305;
the first movable rocker arm 306 can be in contact fit with the first profile 101; the second movable rocker arm 306 may be in contacting engagement with the second profile 102;
the upper end and the lower end of the first movable rocker arm 306 are respectively provided with a first chute 308 and a first locking groove 307; the first inclined groove 308 and the first locking groove 307 are respectively engaged with the first piston rod 317;
the upper end and the lower end of the second movable rocker arm 314 are respectively provided with a second chute 315 and a second locking groove 316; the second inclined groove 315 and the second locking groove 316 can be respectively matched with the second piston rod 318;
by controlling the hydraulic actuator 309, a switching function between the first movable rocker arm 306 in cooperation with the first profile 101 and the second movable rocker arm 306 in cooperation with the second profile 102 is achieved.
One end of the bottom of the rocker arm body 301 is provided with a groove 303 which is matched with the top of the valve 401;
the other end of the bottom of the rocker arm body 301 is provided with a half-moon groove 312 which is matched with the top of the tappet 2;
the first oil channel 201 is communicated with the third oil channel 311 through the half-moon groove 312, and the second oil channel 202 is communicated with the fourth oil channel 313 through the half-moon groove 312;
the third oil passage 311 and the fourth oil passage 313 are externally connected with a three-position four-way solenoid valve;
the first profile 101 has two symmetrical convex ends and the second profile 102 has one convex end;
the wrap angle and the protrusion height of any protrusion end in the first molded line 101 are smaller than those of the second molded line 102;
the rotating speed of the cam 1 is half of the rotating speed of the engine.
The working process of the invention is as follows:
first, taking the two-stroke operation mode as an example, as shown in fig. 1 to 8, at this time, the first locking groove 307 at the lower end of the first movable rocker arm 306 is in contact with the first piston rod 317, the second inclined groove 315 at the upper end of the second movable rocker arm 314 is in contact with the second piston rod 318, the cam 1 is in the base circle state, the cam 1 does not exert a downward action on the first movable rocker arm 306 and the second movable rocker arm 314, the valve 401 abuts against the valve seat 403 under the action force of the valve spring 402, and the valve 401 is in the closed state.
When the cam 1 continues to rotate (clockwise in the front view for example), and both the first profile 101 and the second profile 102 in the cam 1 are in the convex state, as shown in fig. 9 and 10, since the first locking groove 307 at the lower end of the first movable rocker arm 306 is in contact with and matched with the first piston rod 317, the first movable rocker arm 306 is in the locked state, the first profile 101 in the cam 1 will apply a downward acting force to the first movable rocker arm 306, and the valve 401 is in the open state against the acting force of the valve spring 402 through the lever principle of the tappet 2. Because the rotating speed of the cam 1 is half of the rotating speed of the engine, and the first molded line 101 is in a double-peach-point shape, the first molded line 101 in the cam 1 drives the first movable rocker arm 306 once every time the engine rotates, and the working mode of the engine is two-stroke. Since the second inclined groove 315 at the upper end of the second movable rocker arm 314 is in contact engagement with the second plunger 318, the second movable rocker arm 314 is always out of contact with the second profile 102 during the two-stroke mode of operation of the engine.
When the engine needs to be switched from the two-stroke mode to the four-stroke mode, firstly, the engine is operated to a valve closing state, and when the cam 1 continues to rotate clockwise, the first profile 101 is about to bulge, and the second profile 102 is in a base circle state, as shown in fig. 11, at this time, by using an externally-connected three-position four-way solenoid valve, the position of a piston 310 in a hydraulic actuator 309 is adjusted by controlling the direction of hydraulic fluid in a first oil channel 201, a second oil channel 202, a third oil channel 311 and a fourth oil channel 313, the piston is moved to the right side of fig. 11, a first piston rod 317 is separated from a first locking groove 307, and a second piston rod 318 is separated from a second inclined groove 315, so that a second movable rocker arm 314 moves upwards under the action of a spring 304 until the second movable rocker arm is in contact with the base circle portion.
When the cam 1 continues to rotate clockwise to the position shown in fig. 12, the first profile 101 is in the convex state, the second profile 102 is in the base circle state, the first movable rocker arm 306 is driven by the first profile 101 to rotate clockwise around the rocker arm shaft 305, at this time, an externally-connected three-position four-way solenoid valve is utilized, by controlling the direction of the hydraulic fluid in the first oil passage 201, the second oil passage 202, the third oil passage 311 and the fourth oil passage 313, the position of the piston 310 in the hydraulic actuator 309 is adjusted, moving to the left in fig. 12, the first inclined groove 308 at the upper end of the first movable rocker arm 306 is in contact engagement with the first piston rod 317, and as the piston 310 moves further to the left, the first movable rocker arm 306, under the influence of the first angled slot 308, rotates further clockwise about the rocker shaft 305, and gradually out of contact with said first profile 101, as shown in fig. 13, at which point the movement of the first profile 101 will no longer have an effect on the first movable rocker arm 306. At the same time, as the piston 310 moves toward the valve 401, the second plunger rod 318 will engage the second detent groove 316 at the lower end of the second movable rocker arm 314, and the second movable rocker arm 314 is locked.
As the cam continues to rotate clockwise to the position of fig. 14, with both the first profile 101 and the second profile 102 raised, the second profile 102 will exert a downward force on the second movable rocker arm 314, and the valve 401 is opened against the force of the valve spring 402 by the lever principle of the tappet 2. Since the rotation speed of the cam 1 is half of the rotation speed of the engine and the second profile 102 is in the shape of a single-peach-shaped peak, the second profile 102 in the cam 1 will drive the second movable rocker arm 314 once per engine revolution, and the engine operation mode is four-stroke. Since the first inclined groove 308 at the upper end of the first movable rocker arm 306 is in contact fit with the first piston rod 317, the first movable rocker arm 306 is always out of contact with the first profile 101 during the four-stroke operation mode of the engine.
When the engine needs to be switched from the four-stroke mode to the two-stroke mode, the engine is firstly operated to a valve closing state, and when the cam 1 continues to rotate clockwise, the first profile 101 and the second profile 102 are all in a convex state, as shown in fig. 15, at this time, the position of a piston 310 in a hydraulic actuator 309 is adjusted by using an externally-connected three-position four-way electromagnetic valve through controlling the directions of hydraulic fluids in a first oil channel 201, a second oil channel 202, a third oil channel 311 and a fourth oil channel 313, the piston moves to the right side of fig. 15, a first piston rod 317 is separated from a first chute 308, and then a first movable rocker arm 306 moves upwards under the action of a spring 304 until the first movable rocker arm is in contact with a base circle part of the first profile 101. While disengaging the second piston rod 318 from the second locking groove 316.
Since the wrap angle and the protrusion height of any protruding end in the first profile 101 are smaller than those of the second profile 102, when the cam 1 continues to rotate clockwise, it is inevitable that the second profile 102 enters the protruding state before the first profile 101, as shown in fig. 16 and 17, at this time, by using the external three-position four-way solenoid valve, the position of the piston 310 in the hydraulic actuator 309 is adjusted by controlling the directions of hydraulic fluids in the first oil passage 201, the second oil passage 202, the third oil passage 311 and the fourth oil passage 313, and moving to the left side of fig. 16, the first piston rod 317 is in contact fit with the first locking groove 307, the first movable rocker arm 306 is in the locking state, and the second piston rod 318 is in contact fit with the second chute 315. When the cam 1 continues to rotate clockwise, it is shown in fig. 9 and 10. This is repeated.
In conclusion, the position of the piston in the hydraulic actuating mechanism is controlled timely, the matching rule between the piston rod and the movable rocker arm is changed, the rocker arm can be switched, and the two-stroke and four-stroke variable mode is achieved. The invention only needs one hydraulic actuating mechanism, does not need to operate the control mechanism under each working cycle, but can be adjusted under the working condition that the stroke needs to be changed, the control is simple, and when one movable rocker arm is matched with the cam, the other movable rocker arm is not in contact with the cam, the abrasion is reduced, and the invention is beneficial to the engineering application of the variable valve technology.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (2)
1. The utility model provides a high compact rocking arm auto-change over device of engine which characterized in that: comprises a cam (1), a tappet (2), a rocker arm mechanism (3) and an air valve component (4);
a first molded line (101) and a second molded line (102) are arranged on the outer surface of the cam (1);
the rocker arm mechanism (3) comprises a rocker arm body (301), a first movable rocker arm (306) and a second movable rocker arm (314) which are respectively positioned at two sides of the rocker arm body (301); one end of the first movable rocker arm (306) and one end of the second movable rocker arm (314) are both hinged with the rocker arm body (301) through a rocker arm shaft (305);
the first movable rocker arm (306) is in contact fit with the first profile (101); the second movable rocker arm (314) can be in contact fit with the second profile (102);
a hydraulic actuating mechanism (309) is arranged in the rocker arm body (301), and mutual switching between the matching of the first movable rocker arm (306) and the first molded line (101) and the matching of the second movable rocker arm (306) and the second molded line (102) is realized by controlling the hydraulic actuating mechanism (309);
the valve assembly (4) comprises a valve (401), a valve spring (402) and a valve seat (403);
one end of the bottom of the rocker arm body (301) is matched with the top of the valve (401);
a first oil duct (201) and a second oil duct (202) are arranged in the tappet (2); the hydraulic actuator (309) includes a piston (310), a third oil passage (311), and a fourth oil passage (313);
a first piston rod (317) and a second piston rod (318) are arranged on one side, close to the valve assembly (4), of the piston (310); the first movable rocker arm (306) is matched with a first piston rod (317); the second movable rocker arm (314) is engaged with the second piston rod (318);
the other end of the bottom of the rocker arm body (301) is provided with a half-moon groove (312) which is matched with the top of the tappet (2); the first oil channel (201) is communicated with the third oil channel (311) through the crescent groove (312), and the second oil channel (202) is communicated with the fourth oil channel (313) through the crescent groove (312);
the third oil channel (311) and the fourth oil channel (313) are externally connected with a three-position four-way electromagnetic valve;
the upper end and the lower end of the first movable rocker arm (306) are respectively provided with a first chute (308) and a first locking groove (307); the first inclined groove (308) and the first locking groove (307) are respectively matched with the first piston rod (317);
the upper end and the lower end of the second movable rocker arm (314) are respectively provided with a second inclined groove (315) and a second locking groove (316); the second inclined groove (315) and the second locking groove (316) can be respectively matched with the second piston rod (318);
bosses (302) are arranged on two sides of the bottom of the rocker arm body (301); a spring (304) is arranged between the boss (302) and the bottoms of the first movable rocker arm (306) and the second movable rocker arm (314);
said first profile (101) having two symmetrical convex ends and said second profile (102) having one convex end; the wrap angle and the protrusion height of any protrusion end in the first molded line (101) are smaller than those of the second molded line (102);
the rotating speed of the cam (1) is half of the rotating speed of the engine.
2. The engine high compactness rocker arm switching device of claim 1, wherein: one end of the bottom of the rocker arm body (301) is provided with a groove (303) which is matched with the top of the valve (401).
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| CN201811279704.1A CN109630229B (en) | 2018-10-30 | 2018-10-30 | High-compact rocker arm switching device of engine |
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| CN201811279704.1A CN109630229B (en) | 2018-10-30 | 2018-10-30 | High-compact rocker arm switching device of engine |
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| CN109630229A CN109630229A (en) | 2019-04-16 |
| CN109630229B true CN109630229B (en) | 2020-05-26 |
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| CN106545380A (en) * | 2016-12-13 | 2017-03-29 | 大连理工大学 | A kind of locking-type multi-mode lever Variabale valve actuation system |
| CN207122337U (en) * | 2017-09-07 | 2018-03-20 | 吉林大学 | A kind of variable stroke engine valve actuator |
| CN108506063A (en) * | 2018-03-05 | 2018-09-07 | 中国北方发动机研究所(天津) | A kind of two or four stroke hydraulic variable valve mechanism of no valve spring engine |
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