CN101131109A - Air distribution system and method thereof - Google Patents
Air distribution system and method thereof Download PDFInfo
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- CN101131109A CN101131109A CNA2007101757451A CN200710175745A CN101131109A CN 101131109 A CN101131109 A CN 101131109A CN A2007101757451 A CNA2007101757451 A CN A2007101757451A CN 200710175745 A CN200710175745 A CN 200710175745A CN 101131109 A CN101131109 A CN 101131109A
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- valve
- plunger
- oil
- electromagnetic valve
- rocker arm
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Abstract
The present invention discloses one kind of gas distributing system and method. The gas distributing system has one oil feeding path and one oil outlet path communicated to the hydraulic oil source separately, one third oil path communicated to the oil passage inside the plunger sleeve, one first solenoid valve connected to the oil feeding path and the third oil path, one second solenoid valve connected to the oil outlet path and the third oil path, one plunger inside the plunger sleeve, two gas valves connected with one valve bridge, and other parts. The gas distributing system in the technological scheme of the present invention has no rotating part for driving gas valve and improved gas filling efficiency of engine.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a gas distribution system and a gas distribution method.
Background
In a traditional valve actuating mechanism, an engine crankshaft rotates through a valve actuating camshaft driven by a timing gear, and a cam on the valve actuating camshaft drives a valve actuating group to act, so that the valve actuating group is driven to act. The opening and closing process of the valve mechanism is ensured by the cam profile on the cam shaft, and the opening and closing time of the valve is completed by accurately positioning a crankshaft and a pair of timing gears on the cam shaft.
The invention relates to an electronic control hydraulic drive cam-free valve actuating mechanism which is researched and invented on the basis of a novel power device, namely a hydraulic free piston engine. The hydraulic free piston engine is one new type of engine with integrated reciprocating piston type internal combustion engine and plunger type hydraulic pump. The main structural difference from the traditional crankshaft type engine is as follows: the engine does not have a crank mechanism, i.e., a rotating mechanism. Because a rotating mechanism is not arranged, the driving and the timing of the engine valve actuating mechanism are difficult to realize if the valve actuating camshaft of the traditional engine is adopted for driving, so that a valve actuating mechanism without a camshaft is required to realize the air exchange process of the engine.
Disclosure of Invention
The invention aims to provide a valve distribution system and a method, which not only can drive a valve without using a rotating part, but also can effectively improve the charging efficiency of an engine.
In order to achieve the purpose, the invention adopts the following technical scheme:
a gas distribution system is suitable for a hydraulic free piston engine and comprises an oil inlet oil duct 12, an oil outlet oil duct 13, a first switch electromagnetic valve 2, a second switch electromagnetic valve 3, a third oil duct 15, a plunger sleeve 4, a plunger 5, a tappet 7, a push rod 8, a rocker arm 9, a valve bridge 19, two valve springs 10 and two homonymous valves 11, wherein the oil inlet oil duct and the oil outlet oil duct are respectively communicated with a hydraulic oil source system 1 of the hydraulic free piston engine and used for supplying and returning high-pressure oil, the first switch electromagnetic valve, the second switch electromagnetic valve and the plunger sleeve are installed on a machine body 16, one end of the first switch electromagnetic valve is connected with the oil inlet oil duct, the other end of the first switch electromagnetic valve is connected with the third oil duct, one end of the second switch electromagnetic valve is connected with the oil outlet oil duct, the other end of the second switch electromagnetic valve is connected with the third oil duct, the other end of the third oil duct is communicated with the oil duct in the plunger sleeve, the plunger is installed in the plunger sleeve, one end of the plunger corresponds to a roller of the tappet, the lower end of the push rod is connected with one end of the valve bridge through a hinge, and the rocker arm is connected with the upper end of the valve spring, and the valve spring is connected with the upper end of the rocker arm, and the valve spring.
And the valve clearance adjusting screw 18 is positioned on the push rod and used for adjusting the length of the push rod.
The plunger is T-shaped, and the diameter of the section of the upper end of the plunger is larger than that of the section of the lower end of the plunger.
The upper end of the valve spring is arranged at the tail end of the valve through a spring retainer, and the lower end of the valve spring is propped against the cylinder cover 17.
The relationship between the diameter of the plunger and the provided high pressure oil pressure and the stiffness of the valve spring isWherein d represents the plunger diameter, P represents the high oil pressure, and F represents the valve spring force;
the length of the plunger and the relation between the maximum lift of the valve and the minimum height required for guiding are s = h max λ, l.gtoreq.1.5 d, where h max Denotes the maximum valve lift, s denotes the plunger lift, λ denotes the rocker ratio, and l denotes the minimum length required for normal plunger guidingDegree, d represents the plunger diameter, and the plunger length is max { s, l };
and the flow of the oil outlet passage is not less than that of the second switch electromagnetic valve.
The first switch electromagnetic valve, the second switch electromagnetic valve and the plunger sleeve are installed on the machine body through threads.
The plunger sleeve is of a tubular structure, an inner hole is matched with the surface of the plunger, a stepped shaft type structure is arranged outside the plunger sleeve, an external thread is arranged on the upper part with a larger external diameter, an inner hexagonal pit is arranged on the inner hole circle as an inscribed circle, a fastening thread is conveniently installed by a wrench, an internal thread is arranged at a corresponding position on the machine body, and the plunger sleeve is installed on the machine body through the thread.
A method of distributing gas comprising the steps of:
A. the first switch electromagnetic valve is electrified and opened, and the second switch electromagnetic valve is closed;
B. high-pressure oil enters the plunger sleeve through the oil inlet duct and the first switching electromagnetic valve;
C. the high-pressure oil pushes the plunger to move upwards along the plunger sleeve;
D. the plunger pushes the tappet to move upwards, and the tappet drives the push rod to move upwards;
E. the push rod pushes the rocker arm to rotate clockwise around the axis of the rocker arm, and the other end of the rocker arm moves downwards;
F. the rocker arm pushes the valve bridge to drive the two valves with the same name to move downwards, the valves are opened, and the valve springs sleeved on the valves are compressed;
G. when the valve is opened to a set maximum lift, the first switching electromagnetic valve is powered off, the oil inlet duct is closed, and the valve is kept in an opening state;
H. when the valve needs to be closed, the second switch electromagnetic valve is electrified and opened, and high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet duct through the second switch electromagnetic valve;
I. the valve spring extends to drive the valve to seat, and the rocker arm rotates anticlockwise around the axis of the rocker arm;
J. the push rod, the tappet and the plunger return to the original positions under the driving of the rocker arm.
And in the step H, the second switch electromagnetic valve is powered on and opened for a preset time and then is powered off, partial high-pressure oil in the plunger sleeve flows back to the oil tank through the second switch electromagnetic valve via the oil outlet duct, the second switch electromagnetic valve is powered on and opened again after the preset time, and residual high-pressure oil in the plunger sleeve flows back to the oil tank through the second switch electromagnetic valve via the oil outlet duct.
The tappet roller is contacted with the top plane of the plunger piston in the initial installation state by adjusting the valve clearance adjusting screw.
By adopting the technical scheme of the invention, the air distribution system is driven by electronic control hydraulic pressure, so that a rotating part can be avoided, the engine without a rotating mechanism is practical, and the inflation efficiency of the engine can be effectively improved.
Drawings
FIG. 1 is a schematic diagram of a gas distribution system in an embodiment of the present invention;
fig. 2 is a schematic structural diagram of an air distribution system in the embodiment of the present invention.
Detailed Description
The technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings.
The general idea of the invention is: the motion of a hydraulic plunger driven by hydraulic pressure and moving according to a certain rule in a plunger sleeve is utilized to replace the action of the driving force of a cam on a cam shaft in the traditional valve actuating mechanism, and the motion rule of the hydraulic plunger is realized by the action of a switch electromagnetic valve connected in series in a hydraulic loop.
Fig. 1 is a schematic diagram of an air distribution system in an embodiment of the present invention. As shown in fig. 1, a hydraulic oil source system 1 may be generated using output hydraulic energy of a hydraulic free piston engine, and a switching solenoid valve 2 and a switching solenoid valve 3 are connected to the hydraulic oil source system, respectively. When the engine piston is located at a position where the valve needs to be opened, the switch electromagnetic valve 2 for controlling oil inlet is electrified to be opened, high-pressure oil enters the plunger sleeve 4, the switch electromagnetic valve 3 for controlling oil outlet is in a closed state at the moment, therefore, under the action of the high-pressure oil, the plunger 5 can overcome the elastic force of the valve spring 10 to move upwards to push the tappet 7 to move upwards, the tappet pushes the push rod 8 to move upwards, the push rod moves upwards to enable the rocker arm 9 to rotate anticlockwise, the valve spring 10 is compressed to enable the valve 11 to move downwards, the valve is opened, when the valve reaches a set maximum lift, the switch electromagnetic valve 2 is powered off to be closed, because both the switch electromagnetic valves are in a closed state at the moment, the high-pressure oil pressure is maintained in the plunger sleeve, the valve is in an instantaneous balance state, namely, the valve is in the maximum lift, when the piston in the cylinder moves to the position where the valve needs to be closed, the switch electromagnetic valve 3 for controlling oil outlet is electrified to be opened, the high-pressure oil in the plunger sleeve 4 flows back to the oil tank through the switch electromagnetic valve 3, and the plunger is seated under the action of the valve spring 10, and one-time valve opening and closing action is completed.
Fig. 2 is a schematic structural diagram of an air distribution system in the embodiment of the present invention. As shown in fig. 2, the switch solenoid valve 2 is connected with a hydraulic oil source system through an oil inlet duct 12, the switch solenoid valve 3 is connected with the hydraulic oil source system through an oil outlet duct 13, and the two switch solenoid valves are fastened on an engine body 16 in a threaded connection mode, and are fast large-flow solenoid valves, the response time is not more than 3 milliseconds, and the flow is not less than 20 liters per minute. The oil inlet passage 12 and the oil outlet passage 13 are arranged at corresponding positions on the machine body in a drilling mode, and the diameter of the high-pressure oil inlet passage depends on the spring force of the valve, the spring force of the push rod, the lift of the valve and other factors. The diameter of the oil inlet duct is larger than that of the oil duct of the electromagnetic valve, so that throttling action is prevented from being generated, the opening instantaneity of the valve is influenced, meanwhile, the diameter of the oil inlet duct cannot be too large, a large volume effect can be generated, the opening and closing instantaneity of the valve can also be influenced, and the diameter of the oil outlet duct is larger than that of the oil inlet duct. In addition, the diameter of the oil outlet passage depends on the flow of the used solenoid valve, namely the flow of the oil outlet passage is not less than the flow of the solenoid valve.
Plunger bushing 4 passes through the screw thread to be installed on organism 16, the plunger bushing is tubular structure, the hole is high accuracy and plunger cooperation cylindrical surface, the outside is the shaft type structure of ladder, the external screw thread is processed out on the great upper portion of external diameter to in the hole circle is interior regular hexagon pit of inscribed circle processing, be convenient for with spanner installation fastening screw thread, the internal thread is processed out to installation plunger bushing relevant position on the organism, the plunger bushing passes through the screw thread to be installed on the organism, plunger bushing axial position can be through the gasket thickness adjustment on the plunger bushing bottom surface.
The oil passages of the two switching electromagnetic valves are respectively communicated with the oil passages in the plunger sleeve 4 through oil passages 15 processed in the machine body, the position of the plunger sleeve 4 corresponds to a roller of the tappet 7, the plunger 5 is installed in the plunger sleeve 4 through clearance fit, the diameter of the plunger is calculated according to the provided high-pressure oil pressure and the rigidity of the valve spring, and the relation between the diameter of the plunger and the provided high-pressure oil pressure and the rigidity of the valve spring is
Where d represents the plunger diameter, P represents the high oil pressure, and F represents the valve spring force.
The length of the plunger is determined according to the maximum stroke of the valve and the minimum height required by guiding, and the relation between the length of the plunger and the maximum lift of the valve and the minimum height required by guiding is s = h max λ, l.gtoreq.1.5 d, where h max Denotes the maximum valve lift, s denotes the plunger lift, λ denotes the rocker ratio, l denotes the minimum length required for normal guiding of the plunger, d denotes the plunger diameter, and the plunger length is max { s, l }.
The diameter of the head of the plunger is larger than that of the lower part of the plunger, so that the contact transmission force with a tappet roller wheel is convenient, and the contact between the tappet roller wheel and the top plane of the plunger is ensured in an initial installation state by adjusting a valve clearance adjusting screw 18, the lower end of a push rod 8 is placed in a tappet 7, the upper end of the push rod is connected with a rocker arm 9 through the valve clearance adjusting screw, the other end of the rocker arm is hinged with a valve bridge 19 through a hinge, the valve bridge can ensure that two homonymous valves 11 are synchronously driven, a valve spring 10 is clamped outside the valve 11, the upper end of the valve spring is installed at the tail end of the valve through a spring seat ring, the lower end of the valve spring is propped against a cylinder cover 17, and the valve is ensured to be quickly seated.
The specific implementation steps of the electronic control hydraulic drive gas distribution system on the hydraulic free piston engine comprise: when the piston moves to a position where the valve needs to be opened, the switching electromagnetic valve 2 for controlling oil inlet is electrified and opened, high-pressure oil flows through the switching electromagnetic valve 2 through the oil outlet oil duct 12 and the oil duct 15 to enter the plunger sleeve 4, and the switching electromagnetic valve 3 is in a closed state at the moment, so that the high-pressure oil pushes the plunger 5 to move upwards along the plunger sleeve 4 by overcoming the elastic force of the valve spring 10, the plunger 5 pushes the tappet 7 to move upwards, the tappet 7 drives the push rod 8 to move upwards, under the action of the push rod 8, the rocker arm 9 rotates clockwise around the axis of the rocker arm 9, the rocker arm bridge 19 moves downwards, the valve 11 is pushed to move downwards by overcoming the elastic force of the valve spring 10, and the valve is opened. When the valve is opened to the set maximum lift, the switch electromagnetic valve 2 is powered off and closed, and at the moment, the switch electromagnetic valve 3 is in a closed state, so that the pressure of high-pressure oil is kept unchanged in the whole oil duct 15 and the plunger sleeve 4, and the valve is in a balanced state under the combined action of the high-pressure oil and the valve spring, namely the valve is in an open state.
When the valve needs to be closed, the electromagnetic valve 3 is electrified to be opened, high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet duct 13 through the switch electromagnetic valve 3, the pressure is instantaneously reduced, the valve starts to be seated under the action of the valve spring, the rocker rotates anticlockwise around the axis of the rocker, and the push rod, the tappet and the plunger return to the original positions under the driving of the rocker.
In order to prevent valve seating impact, the valve can be closed by adopting a method of closing the valve in sections twice, namely the switch electromagnetic valve 3 is electrified and opened for a preset time and then loses electricity, high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet duct 13 through the switch electromagnetic valve 3, the switch electromagnetic valve 3 is electrified and opened again after a preset time, and residual high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet duct through the switch electromagnetic valve 3, so that the action of opening and closing the valve is completed.
While the invention has been described with reference to specific preferred embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted without departing from the true scope of the invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (10)
1. The air distribution system is suitable for a hydraulic free piston engine and is characterized by comprising an oil inlet channel (12), an oil outlet channel (13), a first switch electromagnetic valve (2), a second switch electromagnetic valve (3), a third oil channel (15), a plunger sleeve (4), a plunger (5), a tappet (7), a push rod (8), a rocker arm (9), a valve bridge (19), two valve springs (10) and two homonymous valves (11), wherein the oil inlet channel and the oil outlet channel are respectively communicated with a hydraulic oil source system (1) of the hydraulic free piston engine and used for supplying and returning high-pressure oil, the first switch electromagnetic valve, the second switch electromagnetic valve and the plunger sleeve are installed on a machine body (16), one end of the first switch electromagnetic valve is connected with the oil inlet channel, the other end of the first switch electromagnetic valve is connected with the third oil channel, one end of the second switch electromagnetic valve is connected with the oil outlet channel, the other end of the second switch electromagnetic valve is connected with the third oil channel, the other end of the third oil channel is connected with the oil outlet channel, one end of the plunger sleeve is connected with the lower end of the tappet and the rocker arm is connected with the lower end of the rocker arm, and the rocker arm is connected with the lower end of the rocker arm.
2. A valve train according to claim 1, further comprising a valve lash adjustment screw (18) located on the push rod for adjusting the length of the push rod.
3. The gas distribution system of claim 1, wherein the plunger is T-shaped with an upper end having a larger cross-sectional diameter than a lower end.
4. A valve train according to claim 1, characterized in that the valve spring is mounted at its upper end to the valve tail end by means of a spring retainer and at its lower end against the cylinder head (17).
5. The gas distribution system of claim 1, wherein the relationship between the diameter of the plunger and the pressure of the high pressure oil supplied and the stiffness of the valve spring is
Wherein d represents the plunger diameter, P represents the high oil pressure, and F represents the valve spring force;
the length of the plunger and the minimum height required by the maximum lift and the guiding of the valve are in a relation of s = h max λ, l.gtoreq.1.5 d, where h max Denotes the maximum lift of the valve, s denotes the plunger lift, and λ denotes the rocker armRatio, l represents the minimum length required by normal guiding of the plunger, d represents the diameter of the plunger, and the length of the plunger is max { s, l };
and the flow of the oil outlet passage is not less than that of the second switch electromagnetic valve.
6. The air distribution system of claim 1, wherein the first switching solenoid valve, the second switching solenoid valve, and the plunger sleeve are threadedly mounted on the housing.
7. The gas distribution system of claim 6, wherein the plunger sleeve is of a tubular structure, the inner hole is a cylindrical surface matched with the plunger, the outer part is of a stepped shaft type structure, the upper part with the larger outer diameter is provided with an external thread, the inner hole circle is an inscribed circle and is provided with an internal regular hexagonal pit, so that a wrench can be used for installing a fastening thread conveniently, an internal thread is arranged at a corresponding position on the machine body, and the plunger sleeve is installed on the machine body through the thread.
8. A gas distribution method is characterized by comprising the following steps:
A. the first switch electromagnetic valve is powered on and opened, and the second switch electromagnetic valve is closed;
B. high-pressure oil enters the plunger sleeve through the oil inlet duct and the first switching electromagnetic valve;
C. the high-pressure oil pushes the plunger to move upwards along the plunger sleeve;
D. the plunger pushes the tappet to move upwards, and the tappet drives the push rod to move upwards;
E. the push rod pushes the rocker arm to rotate clockwise around the axis of the rocker arm, and the other end of the rocker arm moves downwards;
F. the rocker arm pushes the valve bridge to drive the two valves with the same name to move downwards, the valves are opened, and the valve springs sleeved on the valves are compressed;
G. when the valve is opened to a set maximum lift, the first switching electromagnetic valve is powered off, the oil inlet duct is closed, and the valve is kept in an opening state;
H. when the valve needs to be closed, the second switch electromagnetic valve is electrified and opened, and high-pressure oil in the plunger sleeve flows back to the oil tank through the second switch electromagnetic valve and the oil outlet duct;
I. the valve spring extends to drive the valve to be seated, and the rocker arm rotates anticlockwise around the axis of the rocker arm;
J. the push rod, the tappet and the plunger return to the original positions under the driving of the rocker arm.
9. The air distribution method of claim 8, wherein in step H, the second switch solenoid valve is powered on and opened for a predetermined time and then powered off, part of the high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet passage via the second switch solenoid valve, after the predetermined time, the second switch solenoid valve is powered on and opened again, and the residual high-pressure oil in the plunger sleeve flows back to the oil tank through the oil outlet passage via the second switch solenoid valve.
10. The method of claim 8, wherein the tappet roller is brought into contact with the plunger top plane at the initial installation state by adjusting the valve lash adjustment screw.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007101757451A CN100510329C (en) | 2007-10-11 | 2007-10-11 | Air distribution system for hydraulic free piston engine and method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007101757451A CN100510329C (en) | 2007-10-11 | 2007-10-11 | Air distribution system for hydraulic free piston engine and method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101131109A true CN101131109A (en) | 2008-02-27 |
| CN100510329C CN100510329C (en) | 2009-07-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007101757451A Expired - Fee Related CN100510329C (en) | 2007-10-11 | 2007-10-11 | Air distribution system for hydraulic free piston engine and method thereof |
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| Country | Link |
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| CN (1) | CN100510329C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101514645B (en) * | 2008-02-19 | 2012-07-11 | 通用汽车环球科技运作公司 | Oil system for active fuel management on four valve engines |
| CN101960102B (en) * | 2008-03-07 | 2013-08-07 | 欧德克斯有限公司 | Rocker arm unit and method of assembling rocker arm unit |
| CN110173314A (en) * | 2019-05-15 | 2019-08-27 | 浙江大学 | A kind of air valve bridge and its exhaust brake method of achievable compression-release type engine braking |
| CN110185513A (en) * | 2019-07-01 | 2019-08-30 | 贵州大学 | A kind of electric-liquid type variable valve timing regulating device |
| CN111456828B (en) * | 2020-04-23 | 2021-04-16 | 浙江精湛化油器有限公司 | Valve lift adjustable device based on connecting rod transmission principle |
-
2007
- 2007-10-11 CN CNB2007101757451A patent/CN100510329C/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101514645B (en) * | 2008-02-19 | 2012-07-11 | 通用汽车环球科技运作公司 | Oil system for active fuel management on four valve engines |
| CN101960102B (en) * | 2008-03-07 | 2013-08-07 | 欧德克斯有限公司 | Rocker arm unit and method of assembling rocker arm unit |
| CN110173314A (en) * | 2019-05-15 | 2019-08-27 | 浙江大学 | A kind of air valve bridge and its exhaust brake method of achievable compression-release type engine braking |
| CN110173314B (en) * | 2019-05-15 | 2023-07-18 | 浙江大学 | Valve bridge capable of realizing compression release type engine braking and exhaust braking method thereof |
| CN110185513A (en) * | 2019-07-01 | 2019-08-30 | 贵州大学 | A kind of electric-liquid type variable valve timing regulating device |
| CN111456828B (en) * | 2020-04-23 | 2021-04-16 | 浙江精湛化油器有限公司 | Valve lift adjustable device based on connecting rod transmission principle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100510329C (en) | 2009-07-08 |
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Granted publication date: 20090708 Termination date: 20131011 |