CN102852584A - Continuously variable valve lift system - Google Patents
Continuously variable valve lift system Download PDFInfo
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- CN102852584A CN102852584A CN2012103623857A CN201210362385A CN102852584A CN 102852584 A CN102852584 A CN 102852584A CN 2012103623857 A CN2012103623857 A CN 2012103623857A CN 201210362385 A CN201210362385 A CN 201210362385A CN 102852584 A CN102852584 A CN 102852584A
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- 238000004519 manufacturing process Methods 0.000 abstract description 4
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- 230000033228 biological regulation Effects 0.000 description 6
- 230000008569 process Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
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Abstract
The invention discloses a continuously variable valve lift system, which relates to the field of engine valve design; the continuously variable valve lift system comprises a first rocker arm; the bottom side of a first end of the first rocker arm is in contact with a valve and can push the valve; the bottom side of a second end of the first rocker arm is supported by a hydraulic tappet; the continuously variable valve lift system further comprises a second rocker arm which is used for pushing the first rocker arm and driven by a fixedly arranged driving cam; the second rocker arm is arranged on an eccentric wheel and uses the center of the eccentric wheel as rotation center; the position of the rotation center of the second rocker arm is changed; correspondingly, directions and sizes of a power arm and a resisting arm as well as an angle between the second rocker arm and a horizontal plane are changed; and then the rotation quantity of the first rocker arm is driven to be changed; and finally, the lift of the valve in contact with the first rocker arm is changed; and according to the invention, problems of incomplete performance, complicated structure and expensive manufacturing cost of a lifting engine of the traditional valve lift system are solved.
Description
Technical Field
The invention relates to the field of engine valve design, in particular to a continuous variable valve lift system.
Background
For a conventional gasoline engine, the valve lift is fixed, and the engine load is adjusted by controlling the throttle opening. The control method causes the engine to have larger pumping loss, and particularly under partial load, the pumping loss is more serious and can greatly influence the performance of the engine.
Therefore, international large automobile groups invest a great deal of money and manpower to develop the valve lift variable technology. At present, the technology of continuously variable valve lift can change the valve lift according to the operating condition of an engine, so that a throttle valve is always in a range with larger opening, and the characteristics of effectively reducing oil consumption and emission and improving the power and torque of the engine are achieved. However, in the products on the market at present, one type is that the valve lift can be adjusted from two stages to three stages, and the defect is that the performance of the engine can be only partially improved; the other type can realize continuous variable of valve lift, but the mechanism is complex and expensive.
Disclosure of Invention
The invention aims to provide a novel continuous variable valve lift system, which solves the problems of incomplete performance, complex structure and high manufacturing cost of the conventional valve lift system for improving the engine.
In order to achieve the above object, the present invention provides a continuously variable valve lift system, comprising:
the bottom side of the first end of the first rocker arm is in contact with the valve and can push the valve, and the bottom side of the second end of the first rocker arm is supported by the hydraulic tappet;
the driving cam is fixed on the camshaft;
a second rocker arm, the drive cam contacting and pushing a first end of the second rocker arm, a second end of the second rocker arm contacting and pushing the first rocker arm;
the second rocker arm is arranged on the eccentric wheel and takes the center of the eccentric wheel as a rotating center;
the eccentric wheel rotates, the center position of the eccentric wheel is changed, the power arm and the resistance arm of the second rocker arm are correspondingly changed, and finally the lift range of the valve in contact with the first rocker arm is changed.
Optionally, in the above apparatus, the position of the rotation center of the second rocker arm changes, and accordingly the direction and the size of the power arm and the resistance arm, and the included angle between the second rocker arm and the horizontal plane change, and then the rotation amount of the first rocker arm is driven to change, and finally the lift of the valve is changed.
Alternatively, in the above-described apparatus, a drive shaft is arranged in parallel with the camshaft at a predetermined distance, and the eccentric is fixed to the drive shaft.
Optionally, in the above device, the eccentric wheel has a rotation range of 0 ° to 90 °.
Alternatively, in the above device, when the center of the eccentric wheel is located vertically below the axis of the driving shaft, an initial state is defined, in which the power arm is maximum, the resistance arm is minimum, and the valve lift amount is minimum.
When the center of the eccentric wheel rotates to 90 degrees anticlockwise from an initial state, the rotation center of the second rocker arm rises to the highest point of the working state, at the moment, the power arm is minimum, the resistance arm is maximum, and the valve lift is maximum.
Optionally, in the above apparatus, a roller bearing is disposed on the first rocker arm between the first end and the second end, and is configured to be in sliding contact with the second rocker arm.
Optionally, in the above apparatus, a contact portion between the second end of the second rocker arm and the roller bearing is in an inwardly concave arc shape.
Optionally, in the above apparatus, a contact portion between the first end of the second rocker arm and the driving cam is in an inwardly concave arc shape.
Optionally, in the above apparatus, a vertical distance from a rotation center of the second rocker arm to a driving force action line thereof is provided by a power arm, and the driving force is provided by a driving cam;
the vertical distance from the rotating center of the second rocker arm to the acting line of the resistance of the second rocker arm is a resistance arm, and the resistance is generated by the first rocker arm which is pushed by the second rocker arm in a rotating way.
The invention has at least the following technical effects:
1) the position of the rotating center of the second rocker arm is changed by the rotation of the eccentric wheel, so that the direction and the size of a power arm L1 and a resistance arm L2 of the second rocker arm are changed, the lift amount of the valve in contact with the first rocker arm is finally changed, the structure principle is simple, and the control is convenient and quick;
2) according to the invention, the position of the rotating center of the second rocker arm is changed when the eccentric wheel rotates for one angle, so that the lift of the valve is changed, namely, the valve belongs to stepless regulation and control, and the performance of an engine is improved;
3) the range of the rotation angle of the eccentric wheel is only 0-90 degrees, so that the change of the valve lift from minimum to maximum can be realized, and the regulation and control efficiency of the system is higher; the corresponding eccentric wheel rotation control component can be simplified, the manufacture and the installation are easy, and the reliability of the system is improved;
4) the roller bearing is arranged on the first rocker arm, so that the friction between the first rocker arm and the second rocker arm is smaller, and the control efficiency is higher; the contact parts of the second rocker arm, the first rocker arm and the driving cam are designed into concave arcs, and the effect of offsetting or compensating displacement increase and decrease caused by rotation of the second rocker arm is achieved.
Drawings
FIG. 1 is a schematic perspective view of the present invention;
FIG. 2 is a front view of the present invention;
FIG. 3 is a schematic diagram showing the positional relationship of the respective members when the valve lift amounts are respectively minimum and maximum in the present invention;
FIG. 4 is a schematic diagram showing the relationship between the forward and backward positions of the eccentric wheel, the moving direction of the center of the eccentric wheel and the forward and backward positions of the second rocker arm moving along with the eccentric wheel according to the present invention;
FIG. 5 is a schematic diagram of the power arm and the resistance arm when the valve lift amount is minimum in the present invention;
FIG. 6 is a schematic diagram of the power arm and the resistance arm when the valve lift amount is maximum in the present invention;
wherein,
1-second rocker arm, 2-eccentric wheel, 3-hydraulic tappet, 4-driving cam, 5-first rocker arm, 6-valve, 7-driving shaft, 8-camshaft and 9-roller bearing.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the following detailed description of the embodiments is provided with reference to the accompanying drawings.
1-6, embodiments of the present invention provide a continuously variable valve lift system, comprising:
and the bottom side of the first end of the first rocker arm 5 is in contact with the valve 6 and can push the valve 6, and the bottom side of the second end of the first rocker arm 5 is supported by the hydraulic tappet 3, namely, the first rocker arm 5 can rotate around the hydraulic tappet 3.
The drive cam 4 is fixed to a cam shaft 8.
The driving cam 4 contacts and pushes the first end of the second rocker arm 1, the second end of the second rocker arm 1 contacts and pushes the first rocker arm 5, and the pushing force of the valve 6 is provided by the second rocker arm 1.
The second rocker arm 1 is arranged on the eccentric wheel 2, and takes the center of the eccentric wheel 2 as a rotation center.
When the eccentric wheel 2 rotates, the center position of the eccentric wheel 2 is changed, so that the rotation center position of the second rocker arm 1 is changed accordingly, as shown in fig. 4 and 5, the power arm L1 and the resistance arm L2 of the second rocker arm 1 are also changed correspondingly, and finally, the lift of the valve 6 in contact with the first rocker arm 5, namely the valve lift, is changed.
In one embodiment of the invention, a drive shaft 7 may be arranged at a predetermined distance in parallel with the camshaft 8, the eccentric 2 being fixed to the drive shaft 7. As shown in a part a of fig. 4, the change from a solid line to a broken line in the figure is performed in the rotation process of the eccentric wheel 2, the change track of the center of the eccentric wheel 2 is in a circular arc shape, the rotation angle range of the change track is 0-90 degrees, and the valve lift amount also realizes the change from min-max as shown in fig. 3.
As shown by a solid line portion in fig. 3 and fig. 5, an initial state is defined when the center of the eccentric wheel 2 is located vertically below the axial center of the drive shaft 7, i.e., at the position of point a in the portion b of fig. 4. At this time, the power arm L1 is the largest, the resistance arm L2 is the smallest, and the valve lift amount is the smallest.
When the center of the eccentric wheel 2 is gradually raised counterclockwise from the initial state toward the driving cam 4, the rotation center of the second rocker arm 1 rotates and is raised along a circular arc-shaped track, and the moving track is shown by the arrow direction in the part b of fig. 4, so that the second rocker arm 1 moves in both the horizontal and vertical directions. Since the driving cam 4 is fixed and the first rocker arm 5 can rotate around the hydraulic tappet 3, as can be seen from fig. 4 and 5 and the common knowledge of mechanics, the above movement will necessarily cause the angle between the second rocker arm 1 and the horizontal plane to change, at which time the direction of the power arm L1 will change and the power arm L1 will become gradually smaller; in addition, the second end of the second rocker arm 1 must push the first rocker arm 5 to rotate clockwise for a certain angle, at this time, the direction of the resistance arm L2 will be changed, the resistance arm L2 will become gradually larger, accordingly, the rotation amount of the first rocker arm 5 also becomes larger, and finally, the lift amount of the valve 6 arranged at the bottom of the first end of the first rocker arm 5 also becomes gradually larger. As shown in the dotted line portion in fig. 3 and fig. 6, when the rotation angle of the eccentric wheel 2 is 90 °, the rotation center of the second rocker arm 1 rises to the highest point of the operating state thereof, i.e., the position B in the portion B of fig. 4, at this time, the power arm is minimum, the resistance arm is maximum, and the valve lift is maximum. Correspondingly, if the valve lift is to be changed from large to small, the eccentric wheel 2 is rotated clockwise, the principle is the same, the specific process is opposite to the process, and the detailed description is omitted here.
According to the invention, the position of the rotating center of the second rocker arm 1 is changed when the eccentric wheel 2 rotates for one angle, so that the valve lift is changed, namely the system belongs to stepless regulation and control, and the performance of an engine is improved. In addition, the range of the rotation angle of the eccentric wheel 2 is only 0-90 degrees, so that the change of the valve lift from minimum to maximum can be realized, and the regulation and control efficiency of the system is higher; and the corresponding eccentric wheel 2 rotation control component can be simplified, and the manufacture and the installation are easy, and meanwhile, the reliability of the system is also improved.
In one embodiment of the present invention, a roller bearing 9 may be disposed on the first rocker arm 5 between the first end and the second end for sliding contact with the second rocker arm 1, so that the friction between the first rocker arm and the second rocker arm is smaller, and the operation efficiency is higher.
The contact position of the second end of the second rocker arm 1 and the roller bearing 9 and the contact position of the first end of the second rocker arm 1 and the driving cam 4 are both in an inward concave arc shape, and the effect of offsetting or compensating displacement increase and decrease caused by rotation of the second rocker arm is achieved.
In one embodiment of the present invention, the vertical distance from the center of rotation of the second rocker arm 1 to the line of action of its driving force, which is provided by the driving cam 4, is the power arm L1.
The vertical distance from the rotation center of the second rocker arm 1 to the acting line of the resistance is a resistance arm L2, and the resistance is generated by the rotation of the second rocker arm 1 to push the first rocker arm 5.
The invention ensures that the whole working process of the valve lift from minimum to maximum is as follows:
firstly, when the engine runs normally, the driving shaft 8 drives the driving cam 4 to rotate, the driving cam 4 drives the first end of the second rocker arm 1 to enable the second rocker arm 1 to swing around the eccentric wheel 2, and the second end of the second rocker arm 1 drives the first rocker arm 5 to swing around the hydraulic tappet 3, so that the lifting of the valve 6 at the bottom of the first end of the first rocker arm 5 is controlled.
When the stepless regulation is carried out, the corresponding driving device drives the eccentric wheel 2 to rotate anticlockwise from the initial state, and the central position of the eccentric wheel 2 is lifted along the circular arc track every time the eccentric wheel rotates for an angle. At this time, the second rocker arm 1 taking the center of the eccentric wheel 2 as the rotation center is lifted, the second rocker arm 1 is displaced in the horizontal direction and the vertical direction, the fixed driving cam 4 enables the included angle between the second rocker arm 1 and the horizontal plane to be changed, therefore, the direction of the power arm L1 is changed, and the power arm L1 is gradually reduced. Correspondingly, the centre of rotation of second rocking arm 1 risees the in-process, and the second of second rocking arm 1 is held and must will be pushed first rocking arm 5 clockwise and rotate certain angle, and resistance arm L2's direction will change this moment, and resistance arm L2 will grow gradually for the rotation volume grow of first rocking arm 5. Finally, the lift of the valve 6 arranged at the bottom of the first end of the first rocker arm 5 is gradually increased, so that the purpose of stepless regulation of the lift of the valve is achieved, and the performance of the automobile engine is improved. Finally, if the valve lift is to be minimized from the maximum, the above operation process may be reversed, and will not be described herein again.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.
Claims (9)
1. A continuously variable valve lift system, comprising:
the bottom side of the first end of the first rocker arm (5) is in contact with the valve (6) and can push the valve (6), and the bottom side of the second end of the first rocker arm is supported by the hydraulic tappet (3);
a drive cam (4) fixed to the camshaft (8);
a second rocker arm (1), the drive cam (4) contacting and pushing a first end of the second rocker arm (1), a second end of the second rocker arm (1) contacting and pushing the first rocker arm (5);
the second rocker arm (1) is arranged on the eccentric wheel (2) and takes the center of the eccentric wheel (2) as a rotating center;
the eccentric wheel (2) rotates, the center position of the eccentric wheel (2) is changed, the power arm and the resistance arm of the second rocker arm (1) are correspondingly changed, and finally the lift range of the valve (6) in contact with the first rocker arm (5) is changed.
2. The continuous variable valve lift system according to claim 1, characterized in that the position of the center of rotation of the second rocker arm (1) is changed, correspondingly the direction and size of the power arm and the resistance arm, and the included angle between the second rocker arm (1) and the horizontal plane are changed, and then the rotation amount of the first rocker arm (5) is driven to change, and finally the lift of the valve (6) is changed.
3. Continuously variable valve lift system according to claim 1, characterized in that a drive shaft (7) is arranged parallel to the camshaft (8) at a predetermined distance, the eccentric (2) being fixed on the drive shaft (7).
4. Continuously variable valve lift system according to claim 3, characterized in that the rotational range of the eccentric (2) is 0 ° -90 °.
5. The continuous variable valve lift system of claim 4,
when the center of the eccentric wheel (2) is positioned vertically below the axis of the driving shaft (7), an initial state is defined, and at the moment, the power arm is largest, the resistance arm is smallest, and the valve lift is smallest.
When the center of the eccentric wheel (2) rotates to 90 degrees anticlockwise from an initial state, the rotation center of the second rocker arm (1) rises to the highest point of the working state, at the moment, the power arm is minimum, the resistance arm is maximum, and the valve lift is maximum.
6. Continuous variable valve lift system according to claim 1, characterized in that a roller bearing (9) is provided on the first rocker arm (5) between the first and second ends for sliding contact with the second rocker arm (1).
7. The continuous variable valve lift system according to claim 6, characterized in that the second rocker arm (1) has a contact point with the roller bearing (9) in the shape of an inwardly concave arc.
8. The continuous variable valve lift system according to claim 1, characterized in that the contact of the first end of the second rocker arm (1) with the drive cam (4) is in the shape of an inwardly concave arc.
9. The continuous variable valve lift system of claim 1,
the vertical distance from the rotating center of the second rocker arm (1) to the action line of the driving force is a power arm, and the driving force is provided by a driving cam (4);
the vertical distance from the rotating center of the second rocker arm (1) to the acting line of the resistance is a resistance arm, and the resistance is generated by the rotation of the second rocker arm (1) to push the first rocker arm (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210362385.7A CN102852584B (en) | 2012-09-25 | 2012-09-25 | A kind of continuous variable valve lift system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210362385.7A CN102852584B (en) | 2012-09-25 | 2012-09-25 | A kind of continuous variable valve lift system |
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| CN102852584A true CN102852584A (en) | 2013-01-02 |
| CN102852584B CN102852584B (en) | 2016-09-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210362385.7A Expired - Fee Related CN102852584B (en) | 2012-09-25 | 2012-09-25 | A kind of continuous variable valve lift system |
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| CN (1) | CN102852584B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103321708A (en) * | 2013-06-06 | 2013-09-25 | 浙江吉利汽车研究院有限公司杭州分公司 | Stepless variable-valve-lift mechanism |
| CN103437850A (en) * | 2013-08-14 | 2013-12-11 | 重庆长安汽车股份有限公司 | Continuously variable valve lift mechanism |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101457665A (en) * | 2007-12-14 | 2009-06-17 | 现代自动车株式会社 | Continuous variable valve lift system |
| US20100139588A1 (en) * | 2008-12-04 | 2010-06-10 | Hyundai Motor Company | Continuously Variable Valve Lift Apparatus |
| WO2010108374A1 (en) * | 2009-03-27 | 2010-09-30 | 奇瑞汽车股份有限公司 | Engine distribution mechanism with adjustable lift air valve |
| CN102155273A (en) * | 2011-04-08 | 2011-08-17 | 奇瑞汽车股份有限公司 | Variable gas distribution mechanism of engine |
-
2012
- 2012-09-25 CN CN201210362385.7A patent/CN102852584B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101457665A (en) * | 2007-12-14 | 2009-06-17 | 现代自动车株式会社 | Continuous variable valve lift system |
| US20090151665A1 (en) * | 2007-12-14 | 2009-06-18 | Hyundai Motor Company | Continuous variable valve lift system |
| US20100139588A1 (en) * | 2008-12-04 | 2010-06-10 | Hyundai Motor Company | Continuously Variable Valve Lift Apparatus |
| WO2010108374A1 (en) * | 2009-03-27 | 2010-09-30 | 奇瑞汽车股份有限公司 | Engine distribution mechanism with adjustable lift air valve |
| CN102155273A (en) * | 2011-04-08 | 2011-08-17 | 奇瑞汽车股份有限公司 | Variable gas distribution mechanism of engine |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103321708A (en) * | 2013-06-06 | 2013-09-25 | 浙江吉利汽车研究院有限公司杭州分公司 | Stepless variable-valve-lift mechanism |
| CN103321708B (en) * | 2013-06-06 | 2016-06-15 | 浙江吉利汽车研究院有限公司杭州分公司 | Stepless variable valve lift mechanism |
| CN103437850A (en) * | 2013-08-14 | 2013-12-11 | 重庆长安汽车股份有限公司 | Continuously variable valve lift mechanism |
| CN103437850B (en) * | 2013-08-14 | 2015-06-03 | 重庆长安汽车股份有限公司 | Continuously variable valve lift mechanism |
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| CN102852584B (en) | 2016-09-21 |
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Granted publication date: 20160921 |