CN107676144B - Hydraulic variable valve mechanism for 2/4 stroke engine - Google Patents
Hydraulic variable valve mechanism for 2/4 stroke engine Download PDFInfo
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- CN107676144B CN107676144B CN201710927223.6A CN201710927223A CN107676144B CN 107676144 B CN107676144 B CN 107676144B CN 201710927223 A CN201710927223 A CN 201710927223A CN 107676144 B CN107676144 B CN 107676144B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B69/00—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types
- F02B69/06—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types for different cycles, e.g. convertible from two-stroke to four stroke
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention provides a hydraulic variable valve mechanism for an 2/4 stroke engine, which comprises a cam with two types of profiles, a bushing and a piston which are matched with the two types of profiles, and a valve with a pre-tightening spring, wherein the cam is provided with a first cam seat and a second cam seat; by adjusting the magnitude and the direction of the hydraulic pressure in the hydraulic variable valve mechanism, the relative position between the bushing and the piston and the acting force can be changed, and further 2/4 stroke variable and valve lift variable can be realized. The invention does not need to operate the system under each working cycle, but adjusts the parameters under the working condition that the valve motion law needs to be changed, obviously reduces the engine cost and prolongs the service life of components on the basis of ensuring flexible and variable valve motion and compact structure, and 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 hydraulic variable valve mechanism for an 2/4 stroke engine.
Background
Internal combustion engines are still the most thermally efficient prime mover with the greatest power per unit volume and weight, and are widely used, 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. 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.
It is known that, as described in the patent of invention (title: multimode 2-stroke/4-stroke internal combustion engine; patent No. 200880102440.0), the combustion frequency can be doubled by switching the engine stroke from 4-stroke operation to 2-stroke operation, and doubling of the engine power can be achieved even when the output work per cycle is the same. Therefore, it is necessary to develop a compact and flexible variable valve mechanism to achieve the 2/4 stroke interchange function in response to the above-mentioned needs.
Disclosure of Invention
In view of the above, the present invention is directed to a hydraulic variable valve mechanism for an 2/4 stroke engine, which is capable of achieving at least 2/4 stroke interchanging functions, and is compact and flexible.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a hydraulic variable valve mechanism for 2/4 stroke engine comprises a cam, a piston, a bushing and a valve;
the cam surface is provided with two molded lines, namely a first cam molded line matched with the top end of the lining and a second cam molded line matched with the top end of the piston; the first cam profile is in a double-peach shape, and the second cam profile is in a single-peach shape; the rotating speed ratio of the cam to the engine is one to two;
the piston is sleeved in the bushing; the piston head outer rotary surface and the bottom outer rotary surface can respectively slide along the inner wall gap of the bushing; a first hydraulic cavity and a second hydraulic cavity are respectively arranged in the bushing from top to bottom; the side wall of the bushing is also provided with a first channel and a second channel which are used for respectively communicating the first hydraulic cavity and the second hydraulic cavity;
a valve spring is sleeved on a valve rod of the valve; the outer rotary surface of the top end of the valve rod of the valve slides along the gap of the inner wall of the bottom of the piston; a third hydraulic cavity is formed between the top end of the valve rod and the inner wall of the bottom of the piston; and a third channel is also arranged in the piston and used for communicating the first hydraulic cavity with the third hydraulic cavity.
Furthermore, an annular groove is formed in the outer surface of the middle of the piston in the rotating direction, a baffle is arranged inside the bushing, and the baffle divides a space formed by the annular groove and the inner wall of the bushing into a first hydraulic cavity and a second hydraulic cavity from top to bottom.
Furthermore, the top end of the valve rod of the valve is in a shape of a concave piston, the bottom of the piston is in a shape of a piston sleeve, and a third hydraulic cavity is defined by the top end of the valve rod of the valve and the bottom of the piston.
Further, the inner wall of the bottom of the piston is further provided with a first retainer ring for limiting the highest position of the piston sliding relative to the air valve.
Furthermore, a third retaining ring and a second retaining ring are further arranged on the inner wall of the bushing from top to bottom and used for respectively limiting the lowest position and the highest position of the piston relative to the sliding of the bushing.
Furthermore, the first channel and the second channel can be controlled by a common two-position four-way electromagnetic valve externally connected with a high-low pressure oil source for oil return.
Further, the high pressure source pressure is regulated by a conventional high-speed relief valve or common rail system.
Compared with the prior art, the hydraulic variable valve mechanism for the 2/4 stroke engine has the following advantages: the invention can realize 2/4 stroke variable only by adjusting the oil inlet and return direction, and in addition, the maximum lift of the valve can be changed only by adjusting the oil inlet high pressure. The invention does not need to operate the system under each working cycle, but adjusts the parameters under the working condition that the valve motion law needs to be changed, obviously reduces the engine cost and prolongs the service life of components on the basis of ensuring flexible and variable valve motion and compact structure, and 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 schematic diagram of a hydraulic variable valve mechanism for an 2/4-stroke engine with the valve closed under a 4-stroke condition according to the present invention;
FIG. 2 is a schematic diagram of the hydraulic variable valve mechanism for the 2/4 stroke engine with the valve open under a 4-stroke condition according to the invention;
FIG. 3 is a schematic diagram of the hydraulic variable valve mechanism for the 2/4 stroke engine with variable valve lift under a 4-stroke condition according to the invention;
FIG. 4 is a schematic diagram of the 2/4 stroke engine with the hydraulic variable valve mechanism in the 2-stroke condition with the valve closed;
FIG. 5 is a schematic diagram of the 2/4 stroke engine with the hydraulic variable valve mechanism in the 2-stroke condition with the valve open;
FIG. 6 is a schematic diagram of the 2/4 stroke engine with a variable hydraulic valve mechanism with variable valve lift under 2-stroke conditions;
fig. 7 is a front view of a cam in a hydraulic variable valve mechanism for an 2/4 stroke engine according to the present invention;
FIG. 8 is a left side view of FIG. 7;
FIG. 9 is a schematic diagram of the piston in the hydraulic variable valve mechanism for 2/4-stroke engine according to the present invention;
FIG. 10 is a front view of a bushing in the hydraulic variable valve mechanism for 2/4-stroke engine according to the present invention;
FIG. 11 is a left sectional view A-A of FIG. 10;
fig. 12 is a top view of fig. 10.
Description of reference numerals:
1. the hydraulic control valve comprises a cam, 2, a piston, 3, a bushing, 4, a first hydraulic cavity, 5, a second channel, 6, a valve spring, 7, a valve, 8, a second hydraulic cavity, 9, a first channel and 13, and a third hydraulic cavity; 71. a valve stem; 10. a first cam profile, 11 a second cam profile; 21. a third channel, 22. a first retainer ring; 23. a ring-shaped groove; 31. a baffle plate, 32, a second retainer ring, 33, a third retainer ring.
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.
The invention comprises a cam 1, a piston 2, a bush 3 and a valve 7;
the surface of the cam 1 is provided with two molded lines, namely a first cam molded line 10 matched with the top end of the lining 3 and a second cam molded line 11 matched with the top end of the piston 2; the first cam profile is in a double-peach shape, and the second cam profile is in a single-peach shape; the rotating speed ratio of the cam to the engine is one to two; the engine prototype is a 4-stroke engine, the first cam profile 10 and the top end of the bushing 3 can be matched twice in each two-turn engine, and the second cam profile 11 and the top end of the piston 2 can be matched once in each two-turn engine; the piston 2 is sleeved in the bushing 3; the outer revolution surface of the head part and the outer revolution surface of the bottom part of the piston 2 can respectively slide along the inner wall clearance of the bush 3; an annular groove 23 is formed in the outer surface of the middle of the piston 2 in the rotating direction, a baffle 31 is arranged inside the bushing 3, and the baffle 31 divides a space defined by the annular groove 23 and the inner wall of the bushing 3 into a first hydraulic cavity 4 and a second hydraulic cavity 8 from top to bottom; the inner wall of the bushing 3 is also provided with a first channel 9 and a second channel 5 which are respectively communicated with the first hydraulic cavity 4 and the second hydraulic cavity 8; the middle part of a valve rod 71 of the valve 7 is sleeved with a valve spring 6, and the valve spring 6 can provide pretightening force and restoring force; the top end of the valve rod 71 of the valve 7 is in a concave piston shape, the bottom of the piston 2 is in a piston sleeve shape, the top end of the valve rod 71 of the valve 7 and the bottom of the piston 2 enclose a third hydraulic cavity 13, and the outer rotary surface of the top end of the valve rod 71 of the valve 7 slides along the inner wall of the bottom of the piston 2 in a clearance manner; a third channel 21 is further arranged in the piston 2 and is used for respectively communicating the first hydraulic cavity 4 with the third hydraulic cavity 13;
by controlling the direction of movement of the hydraulic fluid in the first and second channels 9, 5, switching between the engagement of the top end of the bushing 3 with the first cam profile 10 and the engagement of the top end of the piston 2 with the second cam profile 11 is possible;
a first retainer ring 22 is further arranged inside the piston 2 and used for limiting the highest position of the piston 2 sliding relative to the valve 7, so that the contact between the piston 2 and the cam 1 when the valve is closed in a 4-stroke mode is avoided, and a large contact stress is generated;
a third retaining ring 33 and a second retaining ring 32 are further arranged on the inner wall of the bushing 3 from top to bottom and used for respectively limiting the lowest position and the highest position of the piston 2 relative to the bushing 3 in a sliding manner, so that the first channel 9 and the second channel 5 are prevented from being blocked in the moving process of the piston 2;
the first channel 9 and the second channel 5 can be controlled by a common two-position four-way electromagnetic valve externally connected with a high-low pressure oil source to perform oil return so as to realize the internal fluid motion of the hydraulic variable valve mechanism;
the pressure of the high-pressure oil source can be adjustable, so that the lift of the valve can be infinitely variable; the high pressure source pressure may be regulated by a conventional high-speed relief valve or common rail system.
The working process of the invention is as follows:
as shown in fig. 1, 2 and 3, the first passage 9 is an oil inlet, and the second passage 5 is an oil return port; the third hydraulic cavity 13 is communicated with an external high-pressure oil source through the third channel 21, the first hydraulic cavity 4 and the first channel 9, and the second hydraulic cavity 8 is communicated with an external low-pressure oil source through the second channel 5; under the action of the hydraulic force, the spaces of the first hydraulic chamber 4 and the third hydraulic chamber 13 are increased, and the space of the second hydraulic chamber 8 is decreased, so that the piston 2 is finally moved upwards and matched with the second cam profile 11 of the cam 1, and meanwhile, the liner 3 is moved downwards and is far away from the first cam profile 10 of the cam 1; in this process, the second stop 32 is used to define the highest position of the piston 2 sliding relative to the bushing 3, avoiding the second channel 5 from being blocked during the movement of the piston 2, while the first stop 22 is used to define the highest position of the piston 2 sliding relative to the valve 7, avoiding the contact between the piston 2 and the cam 1 when the valve is closed, generating a large contact stress.
In fig. 1, since the second cam profile 11 engaged with the piston 2 is in a base circle state and the first retainer 22 defines the highest position of the piston 2 sliding relative to the valve 7, the cam 1 and the piston 2 are not in contact, and only a certain valve clearance is left, so that the cam 1 does not generate driving force for the piston 2, and the valve 7 is in a closed state; in fig. 2, the second cam profile 11 is in a convex state, the acting force on the piston 2 is greater than the pre-tightening force of the valve spring 6, the valve 7 is in an open state, and since the engine prototype is a 4-stroke engine, the second cam profile 11 makes the piston 2 and the valve 7 move once per two revolutions of the engine, thus being in a 4-stroke mode; in fig. 3, the relationship between the hydraulic pressure of the third hydraulic chamber 13 and the spring force of the valve spring 6 can be changed by adjusting the oil inlet pressure of the passage 1, that is, when the oil inlet pressure is properly adjusted to be low, it appears that the cam 1 continues to bulge to move the piston 2 downwards, but at the same time, the volume of the third hydraulic chamber 13 is reduced, and finally, the maximum lift of the valve 7 is reduced; when the oil inlet pressure is increased, the maximum lift of the valve 7 is increased until the first check ring 22 is in contact with the valve 7.
As shown in fig. 4, 5 and 6, the first passage 9 is an oil return port, and the second passage 5 is an oil inlet; the third hydraulic cavity 13 is communicated with an external low-pressure oil source through the third channel 21, the first hydraulic cavity 4 and the first channel 9, and the second hydraulic cavity 8 is communicated with an external high-pressure oil source through the second channel 5; under the action of the hydraulic force, the spaces of the first hydraulic chamber 4 and the third hydraulic chamber 13 are both reduced, and the space of the second hydraulic chamber 8 is increased, so that the piston 2 is finally moved downwards and away from the second cam profile 11 of the cam 1, and meanwhile, the liner 3 is moved upwards and matched with the first cam profile 10 of the cam 1; in the process, the third retainer 33 is used to limit the lowest position at which the piston 2 slides relative to the liner 3, and to prevent the first passage 9 from being blocked during the movement of the piston 2.
In fig. 4, since the space of the third hydraulic chamber 13 is the smallest, the third retainer ring 33 defines the highest position where the liner 3 slides relative to the piston 2, and the first cam profile 10 is in the base circle state, the cam 1 and the liner 3 are not in contact, only a certain valve clearance is left, the cam 1 does not generate driving force for the liner 3, and the valve 7 is in the closed state; in fig. 5, the first cam profile 10 is in a convex state, the acting force on the bush 3 is greater than the pre-tightening force of the valve spring 6, the valve 7 is in an open state, and since the engine prototype is a 4-stroke engine, the first cam profile 10 makes the bush 3 and the valve 7 move twice per two revolutions of the engine, thus being in a 2-stroke mode; in fig. 6, the relationship between the hydraulic pressure of the second hydraulic chamber 8 and the spring force of the valve spring 6 can be changed by adjusting the oil inlet pressure of the second passage 5, that is, when the oil inlet pressure is adjusted to be low, the cam 1 continues to bulge to move the liner 3 downwards, but at the same time, the volume of the second hydraulic chamber 8 is reduced, and finally the maximum lift of the valve 7 is reduced; when the oil inlet pressure is increased, the maximum lift of the valve 7 is increased until the third check ring 33 is in contact with the piston 2.
In summary, the 2/4 stroke can be freely switched only by adopting a common two-position four-way solenoid valve to change and control the oil inlet and return directions of the first passage 9 and the second passage 5; the stepless change of the maximum lift of the valve can be realized only by adopting a common high-speed overflow valve or a common rail system to properly adjust the high pressure of the oil inlet.
The invention does not need to operate the hydraulic system under each working cycle, but adjusts the hydraulic parameters under the working condition that the valve motion law needs to be changed (2/4 stroke switching or when the maximum lift of the valve is changed), obviously reduces the engine cost and prolongs the service life of hydraulic components on the basis of ensuring that the valve motion is flexible and variable, and 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 (7)
1. A hydraulic variable valve mechanism for an 2/4 stroke engine comprises a cam (1), a piston (2) and a bushing (3), wherein the surface of the cam (1) is provided with two types of molded lines, namely a first cam molded line (10) matched with the top end of the bushing (3) and a second cam molded line (11) matched with the top end of the piston (2); the first cam profile (10) is in a double-peach shape, and the second cam profile (11) is in a single-peach shape; the rotating speed ratio of the cam (1) to the engine is one to two; the piston (2) is sleeved in the bushing (3); piston (2) outer surface of revolution of head and the outer surface of revolution of bottom can slide along the inner wall clearance of bush (3) respectively, its characterized in that: also comprises a valve (7);
a first hydraulic cavity (4) and a second hydraulic cavity (8) are respectively arranged in the bushing (3) from top to bottom; the side wall of the bushing (3) is also provided with a first channel (9) and a second channel (5) which are used for respectively communicating the first hydraulic cavity (4) and the second hydraulic cavity (8);
a valve spring (6) is sleeved on a valve rod (71) of the valve (7); the outer rotary surface of the top end of a valve rod (71) of the valve (7) slides along the clearance of the inner wall of the bottom of the piston (2); a third hydraulic cavity (13) is formed between the top end of the valve rod (71) and the inner wall of the bottom of the piston (2); and a third channel (21) is also arranged in the piston (2) and used for communicating the first hydraulic cavity (4) with the third hydraulic cavity (13).
2. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 1, wherein: the piston is characterized in that an annular groove (23) is formed in the outer surface of the middle of the piston (2) in the rotating direction, a baffle (31) is arranged inside the bushing (3), and the space enclosed by the annular groove (23) and the inner wall of the bushing (3) is divided into a first hydraulic cavity (4) and a second hydraulic cavity (8) from top to bottom by the baffle (31).
3. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 1, wherein: the top end of a valve rod (71) of the valve (7) is in a concave piston shape, the bottom of the piston (2) is in a piston sleeve shape, and a third hydraulic cavity (13) is defined by the top end of the valve rod (71) of the valve (7) and the bottom of the piston (2).
4. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 1, wherein: the bottom inner wall of the piston (2) is further provided with a first retainer ring (22) for limiting the highest sliding position of the piston (2) relative to the air valve (7).
5. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 1, wherein: and a third retaining ring (33) and a second retaining ring (32) are further arranged on the inner wall of the bushing (3) from top to bottom and used for respectively limiting the lowest position and the highest position of the piston (2) relative to the sliding of the bushing (3).
6. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 1, wherein: the first channel (9) and the second channel (5) can be controlled by a common two-position four-way electromagnetic valve externally connected with a high-low pressure oil source to return oil.
7. The hydraulic variable valve mechanism for an 2/4-stroke engine according to claim 6, wherein: the high pressure source pressure is regulated by a conventional high speed relief valve or common rail system.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710927223.6A CN107676144B (en) | 2017-09-30 | 2017-09-30 | Hydraulic variable valve mechanism for 2/4 stroke engine |
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| CN201710927223.6A CN107676144B (en) | 2017-09-30 | 2017-09-30 | Hydraulic variable valve mechanism for 2/4 stroke engine |
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| CN107676144A CN107676144A (en) | 2018-02-09 |
| CN107676144B true CN107676144B (en) | 2019-12-27 |
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Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108412574B (en) * | 2018-03-05 | 2019-06-04 | 中国北方发动机研究所(天津) | A kind of mechanical type variable valve mechanism |
| CN108506063B (en) * | 2018-03-05 | 2019-10-25 | 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 |
| CN108412573B (en) * | 2018-03-05 | 2019-07-09 | 中国北方发动机研究所(天津) | A kind of mechanical type variable valve device |
| CN108590801B (en) * | 2018-03-05 | 2020-04-10 | 中国北方发动机研究所(天津) | Hydraulic variable valve lift mechanism of spring engine without valve |
| CN108506059B (en) * | 2018-03-05 | 2019-09-06 | 中国北方发动机研究所(天津) | A kind of mechanical type variable valve driving device |
| CN108894839B (en) * | 2018-06-13 | 2020-04-10 | 中国北方发动机研究所(天津) | Variable valve system of two-four stroke engine |
| CN110454251B (en) * | 2019-08-07 | 2020-11-06 | 中国北方发动机研究所(天津) | Variable valve and variable geometric compression ratio integrated system of diesel engine |
| CN112476299B (en) * | 2020-11-13 | 2022-04-29 | 本田金属技术（佛山）有限公司 | Bushing pressure head structure and using method thereof |
| CN114135402B (en) * | 2021-11-26 | 2023-08-11 | 中国北方发动机研究所(天津) | Two-four stroke variable engine valve mechanism |
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| DE4206166B4 (en) * | 1991-03-14 | 2004-11-04 | Volkswagen Ag | Variable valve train for a lifting valve of a machine |
| JP2004084670A (en) * | 2002-08-28 | 2004-03-18 | Man B & W Diesel As | Valve operated with hydraulic pressure |
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