CN107246294B - A kind of internal combustion engine hydraulic pressure variable valve device - Google Patents
A kind of internal combustion engine hydraulic pressure variable valve device Download PDFInfo
- Publication number
- CN107246294B CN107246294B CN201710409587.5A CN201710409587A CN107246294B CN 107246294 B CN107246294 B CN 107246294B CN 201710409587 A CN201710409587 A CN 201710409587A CN 107246294 B CN107246294 B CN 107246294B
- Authority
- CN
- China
- Prior art keywords
- hydraulic
- valve
- channel
- piston
- bushing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
-
- 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
- F01L9/14—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 the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
Abstract
The present invention provides a kind of hydraulic pressure variable valve devices, including cam, shell, bushing, single-rod piston and hydraulic piston；Bushing, single-rod piston and hydraulic piston are coaxial and can axially move；A unidirectional variable throttle valve and a check valve are equipped with inside hydraulic piston from top to bottom；Single-rod piston and hydraulic piston form a hydraulic cavities, in moving process of the hydraulic piston with cam, the hydraulic cavities or closed or directly or indirectly communicated with outer low pressure oil sources；By the initial position for adjusting outer low pressure oil supply pressure and bushing, thus it is possible to vary the characteristics of motion of hydraulic fluid in the hydraulic cavities, to realize the variable of valve.Present invention eliminates expensive electrohydraulic servo system, guarantees to can obviously reduce cost on the basis of valve motion flexibility and changeability, be conducive to the engineering application of changeable air valve technology.
Description
Technical field
The invention belongs to engine valve structure technical fields, fill more particularly, to a kind of internal combustion engine hydraulic variable valve
It sets.
Background technique
Internal combustion engine is still that thermal efficiency highest, unit volume and the maximum prime mover of power-weight ratio, application are non-so far
Often extensively, however as the gradually shortage and the continuous deterioration of environmental resource of world energy sources, it would be desirable to which internal combustion engine meets more
Stringent emission regulation.Traditional combustion engine takes the camshaft actuated valve of fixed molded line, this makes the discharge of internal combustion engine and oil
Consumption can not reach most preferably in all operating points, and therefore, most internal combustion engine all uses changeable air valve technical controlling to discharge,
Reduce oil consumption.
Changeable air valve technology is broadly divided into variable gas distribution technology based on camshaft and at present without cam distribution technology.The former
It is main to change mechanical structure, therefore structure is simple, fast response time, but because remaining cam, valve is only opposite can
Become, can not arbitrarily can be changed.And it then can arbitrarily change valve timing, lift and duration without cam distribution technology.With regard to driving
Flowing mode divides, and no cam distribution technology is divided into the modes such as electromagnetic drive, electrically driven, motor driven, electro-hydraulic driving.Relative to
The disadvantages of energy consumption is high for electromagnetic drive, and electrically driven response speed is low and unstable, motor-driven system complex, electro-hydraulic drive
It is dynamic it is relatively easy without cam distribution technical pattern, response speed is very fast.However it also have the shortcomings that it is inevitable: under high revolving speed
Flow rate of hydraulic system is inadequate, and valve, which reaches at maximum lift and takes a seat, locates that speed is fast, impact force is big.Therefore it is mainly used for diesel engine
On this lower engine of revolving speed, in addition to this, it is necessary to be using expensive electrohydraulic servo system and relative complex control
Technology processed avoids impact of taking a seat to be accurately controlled valve stroke, and more set solenoid valve systems are needed in Multi-Cylinder Diesel Engine, significantly
Increase the cost of engine.Therefore, flexibility and changeability and the relatively low changeable air valve system suitable for Multi-Cylinder Diesel Engine of cost are studied
It is imperative to unite.
Summary of the invention
In view of this, the present invention is directed to propose a kind of internal combustion engine hydraulic pressure variable valve device, by change bushing with it is hydraulic
The relative position of piston and outer low pressure oil supply pressure, control the movement of hydraulic fluid, final to realize the variable of valve.
In order to achieve the above objectives, the technical scheme of the present invention is realized as follows:
A kind of internal combustion engine hydraulic pressure variable valve device, including cam, shell, bushing, single-rod piston and hydraulic piston；It is described
Upper shell opening, bottom end be equipped with valve port, the bushing in axial direction with the inner sidewall clearance sliding fit of the shell,
The initial position of the bushing is adjustable；The hydraulic piston and single-rod piston are in axial direction between the inner sidewall of the bushing
Gap is slidably matched, and setting up and down, and centre forms hydraulic cavities；
The side wall of the shell is equipped with first passage, and the bushing side wall is equipped with second channel, in the bushing initial bit
It sets in adjustment process, the second channel communicates always with the first passage；It is equipped with from top to bottom inside the hydraulic piston
Unidirectional variable throttle valve and check valve；
The hydraulic piston, in axial direction with bushing inner wall clearance sliding fit, makes described second to lead to the rotation of cam
Road can directly communicate with the hydraulic cavities or mutually break；Or the second channel is made to pass through check valve or unidirectional variable throttle valve and institute
It states hydraulic cavities to communicate or mutually break indirectly, when communicating, hydraulic fluid can flow into described by the check valve in the second channel
Hydraulic cavities, hydraulic fluid flows into the second channel by the unidirectional variable throttle valve in the hydraulic cavities；
Wherein, the unidirectional variable throttle valve can be by changing the pressure between the hydraulic cavities and the second channel
Difference carrys out flow regulating valve aperture；
The upper cover of piston rod of the single-rod piston has valve spring and is fixedly linked with valve, the valve and the shell
The valve port of bottom cooperates；The external low pressure oil sources of first passage, the valve spring provide a pretightning force, the low pressure
The product of oil supply pressure and the single-rod piston sectional area is less than the pretightning force of the valve spring.
Further, control gear is equipped in the shell, the outer surface of the bushing is equipped with one group of vertical direction and institute
The external tooth for stating control gear engagement drives the bushing to slide up and down along the outer casing inner wall by the control gear.
Further, the check valve includes third channel and fourth lane, the third channel and the hydraulic piston
External rotary surface communicate, the fourth lane is communicated with the lower surface of the hydraulic piston, and hydraulic fluid can only be from described
Triple channel flows to the fourth lane；
Further, when the third channel pressure is greater than the fourth lane pressure, the check valve is in open-minded
State, when the third channel pressure is less than the fourth lane pressure, the check valve is in close state；
Further, the unidirectional variable throttle valve include Five-channel, plunger spring, plunger and the 6th channel, the 5th
Channel is communicated with the external rotary surface of hydraulic piston, and the 6th channel is communicated with the lower surface of hydraulic piston, by being arranged the 6th
Channel flows to the plunger spring at Five-channel crossover location, and plunger makes hydraulic fluid that can only flow to the 5th from the 6th channel logical
Road adjusts flow area by the upper and lower position of pilot plunger.
Further, the external low pressure oil sources of the first passage adjusts required confession by overflow valve or throttle valve
Oil pressure, the pressure by adjusting low pressure oil sources control the moving distance of the upper and lower position of plunger.
Compared with the existing technology, present invention has the advantage that
Internal combustion engine hydraulic pressure variable valve device of the present invention, by changing outer low pressure oil supply pressure and bushing axis
To initial position, thus it is possible to vary the characteristics of motion of hydraulic fluid in the hydraulic cavities to realize the flexibility and changeability of valve, and takes
Disappeared expensive electrohydraulic servo system, does not need to operate hydraulic system under each working cycles, but in gas
The door characteristics of motion needs just to be adjusted hydraulic parameter under the operating condition changed, can on the basis of guarantee valve motion flexibility and changeability
It is substantially reduced cost, is conducive to the engineering application of changeable air valve technology, is particularly suitable for multi-cylinder diesel engine.
Detailed description of the invention
The attached drawing for constituting a part of the invention is used to provide further understanding of the present invention, schematic reality of the invention
It applies example and its explanation is used to explain the present invention, do not constitute improper limitations of the present invention.In the accompanying drawings:
Fig. 1 is the signal under hydraulic pressure variable valve device original state (cam does not drive variable valve gear) of the present invention
Figure；
Fig. 2 is schematic diagram when valve will be opened in hydraulic pressure variable valve device of the present invention；
Fig. 3 be in hydraulic pressure variable valve device of the present invention valve stroke and close moment can timing schematic diagram；
Schematic diagram when Fig. 4 is air valve drop in hydraulic pressure variable valve device of the present invention；
Fig. 5 be in hydraulic pressure variable valve device of the present invention valve opening time can timing schematic diagram；
Fig. 6 is the enlarged diagram of hydraulic piston in hydraulic pressure variable valve device of the present invention.
Description of symbols:
1. cam, 2. shells, 3. control gears, 4. bushings, 5. single-rod pistons, 6. valve spring, 7. valves, 8. second is logical
Road, 9. first passages, 10. check valves, 11. hydraulic pistons, 12. unidirectional variable throttle valves, 101. third channels, 102. four-ways
Road, 121. Five-channels, 122. plunger springs, 123. plungers, 124. the 6th channels.
Specific embodiment
It should be noted that in the absence of conflict, the feature in embodiment and embodiment in the present invention can phase
Mutually combination.
The present invention will be described in detail below with reference to the accompanying drawings and embodiments.
A kind of internal combustion engine hydraulic pressure variable valve device of the present invention, as shown in Figures 1 to 6, including cam 1, shell 2, bushing
4, single-rod piston 5 and hydraulic piston 11；2 upper end opening of shell, bottom end are equipped with valve port, and the bushing 4 is in axial direction
With the inner sidewall clearance sliding fit of the shell 2, the initial position of bushing 4 is adjustable；Bushing 4, single-rod piston 5 and the liquid
Press piston 11 coaxial, the hydraulic piston 11 and single-rod piston 5 are in axial direction slided with the inner sidewall gap of the bushing 4
Cooperation, and it is setting up and down, centre forms hydraulic cavities；
The side wall of the shell 2 is equipped with first passage 9, the external low pressure oil sources of the first passage 9；The bushing 4
Side wall is equipped with the second channel 8 being connected to first passage 9, in the 4 initial position adjustment process of bushing, the second channel
8 communicate always with the first passage 9；
Unidirectional variable throttle valve 12 and check valve 10, the check valve 10 are equipped with inside the hydraulic piston 11 from top to bottom
One end is communicated by third channel 101 with the external rotary surface of hydraulic piston 11, and the other end passes through fourth lane 102 and hydraulic work
The lower surface of plug 11 communicates, and hydraulic fluid can only flow to fourth lane 102 from third channel 101；When the third channel 101 is pressed
When power is greater than 102 pressure of fourth lane, the check valve 10 is in opening state, when 101 pressure of third channel is small
When 102 pressure of fourth lane, the check valve is in close state；
The unidirectional variable throttle valve 12 includes Five-channel 121, plunger spring 122, plunger 123 and the 6th channel 124,
Five-channel 121 is communicated with the external rotary surface of hydraulic piston 11, and the 6th channel 124 is communicated with the lower surface of hydraulic piston 11；
The Five-channel 121 lead to upwards equipped with a branched bottom top in the 6th channel 124, plunger spring 122 and plunger 123 according to
The secondary position for being vertically provided at the 6th channel 124 and flowing to the intersection of Five-channel 121, hydraulic fluid can only be flowed from the 6th channel 124
To Five-channel 121, the upper and lower position of plunger 123 is adjustable.
11 upper surface of hydraulic piston is contacted with the cam 1, with the rotation of the cam 1, the hydraulic piston
11 with the molded line of the cam 1 in axial direction with the 4 inner wall clearance sliding fit of bushing, make the second channel 8 can be with
The hydraulic cavities directly communicate or mutually break；
Or pass through the second channel 8 between the check valve 10 or the unidirectional variable throttle valve 12 and the hydraulic cavities
It connecing and communicates or mutually break, when communicating, hydraulic fluid can flow into the hydraulic cavities by the check valve 10 in the second channel 8,
Hydraulic fluid flows into the second channel 8 by the unidirectional variable throttle valve 12 in the hydraulic cavities；
By changing the pressure difference between the 6th channel 124 and Five-channel 121, thus it is possible to vary the pressure of plunger spring 122
Contracting amount, so as to change the distance that plunger 123 moves up and down, to realize the variable of flow area；
Specific implementation are as follows: the external low pressure oil sources of the first passage 9 by common overflow valve or throttle valve come
Charge oil pressure required for adjusting can control the moving distance of the plunger 123, i.e., by adjusting the pressure of low pressure oil sources
The throttle opening of the unidirectional variable throttle valve 12 is controlled, so as to realize the variation of valve stroke.
There is a single-rod piston 5 below the hydraulic piston 11, the single-rod piston 5 can be returned in axial direction in bushing 4
Turn surface gap to be slidably matched, the upper cover of piston rod of 5 lower end of single-rod piston has valve spring 6 and is fixedly connected with valve 7, institute
A pretightning force can be provided by stating valve spring 6, and the valve 7 is matched with valve port；
9 outer end of first passage is connected to outer low pressure oil sources, the low pressure oil supply pressure and the single-rod piston section
Long-pending product is less than the pretightning force of the valve spring, should when the active force that the hydraulic piston 11 is not affected by cam 1 moves down
The hydraulic coupling that low pressure oil sources acts on single-rod piston 5 is less than the pretightning force of valve spring 6.Because if low pressure oil sources is made at this time
It is greater than the pretightning force of valve spring 6 for the hydraulic coupling of single-rod piston 5, then valve 10 is in the open state always, it will is sending out
Piston and valve is caused to bump against in motivation operational process, mechanism damage.
Control gear 3 is equipped in the shell 2, the outer surface that 2 inner wall of shell slides up and down bushing 4 is equipped with one group and erects
Histogram is to the external tooth engaged with control gear 3, and control gear 3 drives bushing 4 to slide up and down along 2 inner wall of shell, to change lining
The initial position of set 4.
The course of work of inventive combustion engine hydraulic pressure variable valve device is as follows:
The course of work of the invention is as follows:
In fig. 1, it is assumed that cam 1 rotates clockwise, 1 protruding end of cam and 11 upper surface of hydraulic piston are contactless at this time,
Cam 1 does not drive variable valve gear, and the hydraulic cavities formed between single-rod piston 5 and hydraulic piston 11 pass through second channel respectively
8, first passage 9 is communicated with low pressure oil sources, since the hydraulic coupling that low pressure oil sources acts on single-rod piston 5 at this time is less than valve spring
6 pretightning force, therefore valve 7 is in close state.
When cam 1 continues to rotate clockwise, until cam 1 is opened when 1 protruding end of cam and 11 upper surface of hydraulic piston contact
Begin driving variable valve gear, and hydraulic piston 11 is moved down along axial direction, the hydraulic cavities formed between hydraulic piston 11 and single-rod piston 5
Volume reduces, and the hydraulic fluid in the hydraulic cavities flows into low pressure oil sources from second channel 8, first passage 9, since single pole is living at this time
Initial pretightening force of the hydraulic oil active force suffered by 5 upper surfaces still less than valve spring 6 is filled in, therefore valve 7 is still in closing shape
State.
When cam 1 continues to rotate clockwise, hydraulic piston 11 continues to move down, until 11 lower edge of hydraulic piston and second channel
When 8 lower edges are equal, as shown in Fig. 2, check valve 10 is in close state, an envelope is formed between hydraulic piston 11 and single-rod piston 5
Hydraulic cavities are closed, the oil pressure of the hydraulic cavities increases rapidly in the case where the rotation of cam 1 drives, big to the active force of 5 rear end of single-rod piston
In the pretightning force of valve spring 6, hydraulic piston 11 and single-rod piston 5 move together, and valve 7 is gradually opened.
When cam 1 continues to rotate clockwise, hydraulic piston 11 continues to move down, until one end the of unidirectional variable throttle valve 12
When Five-channel 121 is communicated with second channel 8, as shown in figure 3, the hydraulic cavities warp formed between hydraulic piston 11 and single-rod piston 5
Cross unidirectional variable throttle valve 12, second channel 8 is communicated with low pressure oil sources, hydraulic cavities volume is gradually reduced, cam 1 movement advise
7 lift of valve becomes smaller on the basis of rule.
By adjusting extraneous low pressure oil supply pressure, thus it is possible to vary the pressure difference between hydraulic cavities and the second channel 8, into
And change unidirectional 12 aperture of variable throttle valve, influence the characteristics of motion of 7 lift of valve；Such as when low pressure oil supply pressure becomes larger,
Unidirectional 12 aperture of variable throttle valve becomes smaller, and hydraulic cavities volume reduces amplitude and becomes smaller, and valve maximum lift becomes larger and gas may be implemented
Men Wanguan function；When low pressure oil supply pressure becomes smaller, unidirectional 12 aperture of variable throttle valve becomes larger, and hydraulic cavities volume reduces amplitude and becomes
Greatly, valve maximum lift becomes smaller and valve morning Guan Gongneng may be implemented.
When cam 1 continues to rotate clockwise, hydraulic piston 11 reaches minimum point and then moves up, until when valve 7 is closed, such as
Shown in Fig. 4, cam 1 will continue the hydraulic cavity pressure for rotating clockwise, being formed between hydraulic piston 11 and single-rod piston 5 at this time
Drastically reduce, and lower than extraneous low pressure oil supply pressure, the check valve 10 is in opening state, hydraulic fluid from first passage 9,
Second channel 8, check valve 10 flow into hydraulic cavities, and the continuation of hydraulic piston 11 contacts with cam 1, prevents from being detached from, so as to prepare
Subsequent cycle.
Gear 3 is controlled by adjusting, as shown in fig. 5, it is assumed that control gear 3 rotates counterclockwise, bushing 4 is moved down, and second is logical
The initial distance of 8 lower edge of road to 11 lower edge of hydraulic piston is elongated, and cam 1, which needs to rotate clockwise more perspective, can just make hydraulic work
Closing hydraulic cavities are formed between plug 11 and single-rod piston 5 drives valve 7 to open, to realize that valve evening opens；Conversely, when control tooth
Wheel 3 rotates clockwise, and bushing 4 moves up, and the initial distance of 8 lower edge of second channel to 11 lower edge of hydraulic piston shortens, 1 need of cam
Rotating clockwise less angle can make formation closing hydraulic cavities between hydraulic piston 11 and single-rod piston 5 that valve 7 be driven to open
It opens, to realize that valve is early opened.
To sum up, by adjusting the pressure of low pressure oil sources and controlling rotation angle (the i.e. initial bit of bushing 4 of gear 3
Set), the valve motion rule of flexibility and changeability can be realized.
Present invention eliminates expensive electrohydraulic servo system, do not need under each working cycles to hydraulic system into
Row operation, but just hydraulic parameter is adjusted in the case where valve motion rule needs the operating condition changed, guarantee valve motion spirit
Living can obviously reduce cost on the basis of can be changed, and is conducive to the engineering application of changeable air valve technology, is particularly suitable for multi-cylinder bavin
Oil machine.
The foregoing is merely illustrative of the preferred embodiments of the present invention, is not intended to limit the invention, all in essence of the invention
Within mind and principle, any modification, equivalent replacement, improvement and so on be should all be included in the protection scope of the present invention.
Claims (6)
1. a kind of internal combustion engine hydraulic pressure variable valve device, including cam (1), shell (2), single-rod piston (5) and hydraulic piston
(11)；It is characterized by also including bushing (4), shell (2) upper end opening, bottom end is equipped with valve port, the bushing (4)
In axial direction with the inner sidewall clearance sliding fit of the shell (2), the initial position of the bushing (4) is adjustable；The liquid
Press piston (11) and single-rod piston (5) the in axial direction inner sidewall clearance sliding fit with the bushing (4), and on divide into
It sets, centre forms hydraulic cavities；
The side wall of the shell (2) is equipped with first passage (9), and bushing (4) side wall is equipped with second channel (8), in the lining
It covers in (4) initial position adjustment process, the second channel (8) communicates always with the first passage (9)；The hydraulic piston
(11) internal to be equipped with unidirectional variable throttle valve (12) and check valve (10) from top to bottom；
The hydraulic piston (11) in axial direction with bushing (4) inner wall clearance sliding fit, makes described with the rotation of cam (1)
Second channel (8) can directly communicate with the hydraulic cavities or mutually break；Or the second channel (8) is made to pass through check valve (10) or single
It communicates to variable throttle valve (12) with the hydraulic cavities or mutually breaks indirectly, when communicating, the interior hydraulic fluid of the second channel (8) can
The hydraulic cavities are flowed by the check valve (10), hydraulic fluid passes through the unidirectional variable throttle valve in the hydraulic cavities
(12) second channel (8) are flowed into；
Wherein, the unidirectional variable throttle valve (12) can be by changing between the hydraulic cavities and the second channel (8)
Pressure difference carrys out flow regulating valve aperture；
The upper cover of piston rod of the single-rod piston (5) has valve spring (6) and is fixedly linked with valve (7), the valve (7) with
The valve port of shell (2) bottom cooperates；The external low pressure oil sources of first passage (9), the valve spring (6) provide
The product of one pretightning force, the low pressure oil supply pressure and the single-rod piston (5) sectional area is less than the pre- of the valve spring (6)
Clamp force.
2. internal combustion engine hydraulic pressure variable valve device according to claim 1, it is characterised in that: be equipped in the shell (2)
It controls gear (3), the outer surface of the bushing (4) is equipped with the external tooth that one group of vertical direction is engaged with control gear (3), leads to
Crossing the control gear (3) drives the bushing (4) to slide up and down along the shell (2) inner wall.
3. internal combustion engine hydraulic pressure variable valve device according to claim 1, it is characterised in that: the check valve (10) includes
Third channel (101) and fourth lane (102), the external rotary surface of the third channel (101) and the hydraulic piston (11)
It communicates, the fourth lane (102) communicates with the lower surface of the hydraulic piston (11), and hydraulic fluid can only be logical from the third
Road (101) flows to the fourth lane (102).
4. internal combustion engine hydraulic pressure variable valve device according to claim 3, it is characterised in that: when the third channel
(101) when pressure is greater than the fourth lane (102) pressure, the check valve (10) is in opening state, when the third is logical
When road (101) pressure is less than the fourth lane (102) pressure, the check valve (10) is in close state.
5. internal combustion engine hydraulic pressure variable valve device according to claim 1, it is characterised in that: the unidirectional variable throttle valve
It (12) include Five-channel (121), plunger spring (122), plunger (123) and the 6th channel (124), the Five-channel
(121) it is communicated with the external rotary surface of the hydraulic piston (11), the 6th channel (124) and the hydraulic piston (11)
Lower surface communicates, and flows to the column at Five-channel (121) crossover location in the 6th channel (124) by being arranged
It fills in spring (122), the plunger (123) makes hydraulic fluid that can only flow to the Five-channel from the 6th channel (124)
(121), flow area is adjusted by adjusting the upper and lower position of the plunger (123).
6. internal combustion engine hydraulic pressure variable valve device according to claim 5, it is characterised in that: the first passage (9) is outside
The low pressure oil sources connect adjusts required charge oil pressure by overflow valve or throttle valve, by the pressure control for adjusting low pressure oil sources
Make the moving distance of the upper and lower position of the plunger (123).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710409587.5A CN107246294B (en) | 2017-06-02 | 2017-06-02 | A kind of internal combustion engine hydraulic pressure variable valve device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710409587.5A CN107246294B (en) | 2017-06-02 | 2017-06-02 | A kind of internal combustion engine hydraulic pressure variable valve device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107246294A CN107246294A (en) | 2017-10-13 |
| CN107246294B true CN107246294B (en) | 2019-09-20 |
Family
ID=60017809
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710409587.5A Active CN107246294B (en) | 2017-06-02 | 2017-06-02 | A kind of internal combustion engine hydraulic pressure variable valve device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107246294B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108240244B (en) * | 2017-12-29 | 2023-12-19 | 潍柴动力股份有限公司 | Variable system of diesel engine inlet valve and diesel engine |
| CN108590800B (en) * | 2018-03-05 | 2020-07-24 | 中国北方发动机研究所(天津) | Mechanical variable valve driving mechanism |
| CN111120029A (en) * | 2019-12-26 | 2020-05-08 | 哈尔滨工程大学 | Rotary plunger type fully-variable valve actuating mechanism of internal combustion engine |
| CN111022140B (en) * | 2019-12-26 | 2022-05-10 | 哈尔滨工程大学 | Hydraulically controlled fully-variable valve actuating mechanism of internal combustion engine |
| CN111188662A (en) * | 2020-01-07 | 2020-05-22 | 绵阳华博精工机械有限公司 | Valve mechanism |
| CN112253271B (en) * | 2020-10-23 | 2021-08-31 | 徐州工业职业技术学院 | Hydraulic transmission valve mechanism |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1612428A1 (en) * | 2003-03-24 | 2006-01-04 | Yokohama TLO Company, Ltd., c/o Yokohama National Univ. | Variable valve system of internal combustion engine and hydraulic actuator |
| CN106285816A (en) * | 2015-05-21 | 2017-01-04 | 北京理工大学 | A kind of hydraulic variable valve and control method thereof |
-
2017
- 2017-06-02 CN CN201710409587.5A patent/CN107246294B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1612428A1 (en) * | 2003-03-24 | 2006-01-04 | Yokohama TLO Company, Ltd., c/o Yokohama National Univ. | Variable valve system of internal combustion engine and hydraulic actuator |
| CN1764787A (en) * | 2003-03-24 | 2006-04-26 | 横浜Tlo株式会社 | Variable valve system of internal combustion engine, its control method and hydraulic actuator |
| KR100679594B1 (en) * | 2003-03-24 | 2007-02-08 | 요코하마 티엘오 가부시키가이샤 | Variable valve system of internal combustion engine and control method thereof, and hydraulic actuator |
| US7178489B2 (en) * | 2003-03-24 | 2007-02-20 | Yokohama Tlo Company, Ltd. | Variable valve system of internal combustion engine and hydraulic actuator |
| CN100365292C (en) * | 2003-03-24 | 2008-01-30 | 横浜Tlo株式会社 | Variable valve system of internal combustion engine, its control method and hydraulic actuator |
| CN106285816A (en) * | 2015-05-21 | 2017-01-04 | 北京理工大学 | A kind of hydraulic variable valve and control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107246294A (en) | 2017-10-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107246294B (en) | A kind of internal combustion engine hydraulic pressure variable valve device | |
| CN103277163B (en) | Variable-lift driver | |
| CN107676144A (en) | A kind of 2/4 Stroke Engine hydraulic variable valve mechanism | |
| US7404382B2 (en) | Variable engine valve control system with pressure difference | |
| CN110094244B (en) | Electro-hydraulic fully-variable gas distribution actuator and control method thereof | |
| CN103216290B (en) | Variable lift driver | |
| CN206496055U (en) | A kind of overflow valve based on magnetic rheology effect | |
| CN203009064U (en) | Self-pumping compression ratio adjustable engine piston | |
| CN103174490B (en) | Hydraulic pressure variable valve device based on rotor control | |
| CN108506063B (en) | A kind of two or four stroke hydraulic variable valve mechanism of no valve spring engine | |
| CN107355276B (en) | A kind of variable valve actuator for air of high hydraulic-driven | |
| CN103266927B (en) | Rocker system of hydraulic stepless variable valve | |
| CN207377616U (en) | A kind of hydraulic-driven variable valve actuator for air of low voltage control high pressure | |
| CN107143393B (en) | A kind of internal combustion engine hydraulic variable valve mechanism | |
| CN107060935B (en) | A kind of hydraulic pressure variable valve device | |
| CN205908328U (en) | Four properties door engine variable valve mechanism | |
| CN107842407B (en) | A kind of variable valve actuator for air that 2/4 stroke can be achieved and exchanges | |
| CN207177988U (en) | A kind of electric machine controlled hydraulic-driven variable valve actuator for air | |
| CN108590801A (en) | A kind of no valve spring engine liquid pressure type variable air valve lift range mechanism | |
| CN203201890U (en) | Rotation position and speed compound control hydraulic system during segment assembly | |
| CN101302992A (en) | Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque | |
| CN107013523A (en) | The reversing arrangement and application method of a kind of hydraulic hammer | |
| CN108506059B (en) | A kind of mechanical type variable valve driving device | |
| CN109322719B (en) | Hydraulic variable valve rocker device | |
| CN202832691U (en) | Hydraulic tappet suitable for variable valve timing mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |