CN103953408A - Infinite variable gas distribution timing mechanism - Google Patents
Infinite variable gas distribution timing mechanism Download PDFInfo
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- CN103953408A CN103953408A CN201410180877.3A CN201410180877A CN103953408A CN 103953408 A CN103953408 A CN 103953408A CN 201410180877 A CN201410180877 A CN 201410180877A CN 103953408 A CN103953408 A CN 103953408A
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- plunger
- driven inner
- inner core
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- oil
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- 238000009826 distribution Methods 0.000 title abstract description 5
- 230000005540 biological transmission Effects 0.000 claims abstract description 4
- 238000009827 uniform distribution Methods 0.000 claims description 10
- 238000007789 sealing Methods 0.000 claims description 4
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 230000006837 decompression Effects 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 61
- 238000000034 method Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000006698 induction Effects 0.000 description 2
- 239000010721 machine oil Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
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- Valve Device For Special Equipments (AREA)
Abstract
The invention discloses an infinite variable gas distribution timing mechanism. A mechanical control part comprises a driving outer cylinder, a driven inner cylinder and a plunger, the driving outer cylinder and the driven inner cylinder are coaxially arranged in a sleeving way, the plunger is pushed by an electromagnetic valve, the driving outer cylinder is coaxially fixedly connected with a transmission wheel, a shaft hole at one end of the driven inner cylinder is fixedly connected with one shaft end of a cam shaft, the plunger is fitted in a shaft hole at the other end of the driven inner cylinder in a sliding way, a return spring is pressed between the plunger and the shaft end of the cam shaft, the driving outer cylinder and the driven inner cylinder are transmitted through inner teeth and outer teeth, the inner teeth and the outer teeth are uniformly distributed on the peripheries of the driving outer cylinder and the driven inner cylinder, and an oil cavity with a variable capacity is formed between the driving outer cylinder and the driven inner cylinder. A loop of a hydraulic control part comprises a cam shaft bearing part oil line, a cam shaft end inner oil line, a plunger inner oil line and a radial driven inner cylinder inner oil line uniformly distributed on the periphery, radial pressure relief holes and overflow holes are uniformly formed in the periphery of the plunger, and the pressure relief holes and the overflow holes can be respectively communicated with the driven inner cylinder inner oil line. The capacity size of the oil cavity is regulated through oil pressure, and infinite variable gas distribution timing regulation is realized.
Description
(1) technical field:
The present invention relates to motor car engine air-distributing valve mechanism, be specially a kind of electrodeless variable valve timing mechanism.
(2) background technique:
Different engines distributions are regularly the best valve timings obtaining according to test, thereby the foundation that becomes design Valve-train Cam and determine each cylinder inlet and outlet cam relative position on camshaft, but in fact, when distribution cam axle design fixed, the valve timing of motor has also just been decided, and is unalterable in engine operation process.
Yet the height of engine speed is flowed by inlet and outlet and cylinder combustion burning process is influential.When rotating speed is high, induction air flow ratio is high, and inertia is large, so wish that intake valve opens earlier, close evening, enters some mixed gass or air more as far as possible; Otherwise when engine speed is lower, induction air flow ratio is low, and inertial flow is also little, if intake valve is opened too early, because piston now, just in up exhaust, is easy to live gas to extrude cylinder, air inlet is reduced on the contrary, engine operation is more unstable.Therefore,, when the slow-speed of revolution, wish engine intake valve unlatching a bit a little later.So, when engine speed is different, to the requirement of valve timing, be different.
Since the eighties in last century, there is the control mechanism of some variable valve timings in Ge great automobile production company on motorcar engine.As the VTEC mechanism of Honda Company, changeable air valve timing mechanism of Alfa Romeo company exploitation etc.It is electrodeless variable that but above mechanism all can not realize.
(3) summary of the invention:
For the deficiencies in the prior art, the present invention proposes a kind of electrodeless variable valve timing mechanism, mainly solve in operation process, the valve timing of motor can not electrodeless variable technical problem.
The electrodeless variable valve timing mechanism that can solve the problems of the technologies described above, comprise mechanical control section and hydraulic control part, described mechanical control section comprises the active urceolus of coaxial package and driven inner core and the plunger being promoted by solenoid valve, described active urceolus and drive wheel are coaxially connected, one end axis hole of described driven inner core and camshaft one axle head are coaxially connected, described plunger is coaxially snug fit at driven inner core the other end axis hole, in driven inner core axis hole between plunger and camshaft, press-fit return spring, described active urceolus and driven inner core pass through corresponding in plunger position, external tooth transmission, in described, external tooth circumference uniform distribution setting in active urceolus and on driven inner core, external tooth circumferential size is less than internal tooth circumferential size and the oil pocket of between formation variable volume, the loop of described hydraulic control part comprises the bearing position oil circuit of camshaft, the axle head internal oil passages of camshaft, plunger internal oil passages and corresponding to the radially driven inner core internal oil passages of each oil pocket circumference uniform distribution, on plunger, offer respectively the radially relief hole of circumference uniform distribution and overflow hole radially, described relief hole and overflow hole can be communicated with driven inner core internal oil passages respectively.
Described plunger puts in place to entering in driven inner core, described overflow hole sealing, described relief hole is communicated with driven inner core internal oil passages, each oil pocket oil-feed pressurize, promote external tooth turns an angle in internal tooth, realize driven inner core and drive camshaft to turn an angle forward, thereby control advance angle size.
Described plunger exits driven inner core and puts in place, and described relief hole exposes, and described overflow hole is communicated with driven inner core internal oil passages, each oil pocket draining decompression, and external tooth return, in internal tooth original position, recovers the former working position of cam.
Bearing support is installed the bearing position of described camshaft and by seal ring sealing attachment face, bearing support internal oil passages is communicated with bearing position oil circuit.
Described drive wheel can adopt biserial sprocket wheel.
Beneficial effect of the present invention:
1, the electrodeless variable valve timing mechanism of the present invention can coordinate the displacement of plunger to control oil-feed and the draining of oil pocket by oil hydraulic circuit, and then control the angle of separating between the inside and outside tooth of transmission between driving and driven inner core, thereby reach, the advance angle of intake valve is increased, the corresponding object reducing in the angle that lags.
2, the present invention is by oil pocket volume size between the inside and outside tooth of size adjustment of hydraulic fluid pressure, and then controls camshaft advancement amount in relative rotation, thereby realize electrodeless variable valve timing, regulates.
(4) accompanying drawing explanation:
Fig. 1 is the structural representation of one embodiment of the present invention, forms minimum oil pocket between inside and outside tooth.
Fig. 2 is the A-A cut-away view in Fig. 1.
Fig. 3 is in Fig. 1 mode of execution, forms the structural representation of maximum oil pocket between inside and outside tooth.
Fig. 4 is the B-B cut-away view in Fig. 3.
Figure number sign: 1, active urceolus; 2, driven inner core; 3, solenoid valve; 4, plunger; 5, drive wheel; 6, camshaft; 7, return spring; 8, internal tooth; 9, external tooth; 10, oil pocket; 11, bearing position oil circuit; 12, camshaft axle head internal oil passages; 13, plunger internal oil passages; 14, driven inner core internal oil passages; 15, relief hole; 16, overflow hole; 17, bearing support internal oil passages; 18, seal ring; 19, cam; 20, bearing support.
(5) embodiment:
Below in conjunction with accompanying drawing illustrated embodiment, technological scheme of the present invention is described further.
The electrodeless variable valve timing mechanism of the present invention is mainly partly comprised of mechanical control section and hydraulic control.
1, machinery control section: comprise initiatively urceolus 1, driven inner core 2, solenoid valve 3 and plunger 4, described active urceolus 1 is coaxially fixedly mounted with drive wheel 5 (adopting biserial sprocket wheel), active urceolus 1 and driven inner core 2 coaxial packages, can relatively rotate between the two, and the internal tooth 8 arranging by both left ends and initiatively driven inner core 2 rotations of urceolus 1 drive of external tooth 9 structures realizations, described internal tooth 8 (three) circumference uniform distribution is opened on the inner peripheral surface of active urceolus 1, described external tooth 9 (three) circumference uniform distribution is located on driven inner core 2 excircles, the size of external tooth 9 circumferencial directions is less than the size of internal tooth 8 circumferencial directions, thereby form the oil pocket 10 of variable volume, the left end axis hole of described driven inner core 2 is little and right-hand member axis hole is large, described plunger 4 is snug fit in the little axis hole of driven inner core 2 left end, the outer end of plunger 4 connects the solenoid valve 3 of outer installment, the local large axis hole bottom that is matched with driven inner core 2 that increases, the inner of plunger 4, the macro-axis nose end interference fit of driven inner core 2 is in the left axle head of camshaft 6, the left axle head of described camshaft 6 is installed by bearing support 20, attachment face is provided with seal ring 18, corresponding to valve position, in camshaft 6, be provided with cam 19, between plunger 4 the inners and camshaft 6 axle heads, press-fit return spring 7 in the large axis hole of driven inner core 2, as Fig. 1, shown in Fig. 3.
Described hydraulic control part: its oil hydraulic circuit comprises the bearing internal oil passages 17 that is radially opened in bearing support 20 inside, radially be opened in the bearing position oil circuit 11 of camshaft 6 axle end bearing positions, coaxially be opened in the camshaft axle head internal oil passages 12 of camshaft axle head, coaxially be opened in the plunger internal oil passages 13 (arise from plunger 4 inner and end at plunger 4 outer ends) of plunger 4, in driven inner core 2 inside, offer the radially driven inner core internal oil passages 14 (being communicated with each corresponding oil pocket 10) of circumference uniform distribution, radially overflow hole 16 and the relief hole 15 of the circumference uniform distribution of offering respectively on the cylinder apart from plunger 4 the inners and outer end, as Fig. 1, Fig. 2, Fig. 3, shown in Fig. 4.
Described oil hydraulic circuit has two kinds of paths.
1, under solenoid valve 3 drives and return spring 7 effects, plunger 4 outwards exits driven inner core 2 and puts in place, and described relief hole 15 exposes outside driven inner core 2, overflow hole 16 and the corresponding connection of driven inner core internal oil passages 14.
Oil hydraulic circuit main path is: bearing internal oil passages 17---bearing position oil circuit 11---camshaft axle head internal oil passages 12---the driven large axis hole of inner core 2---plunger internal oil passages 13---relief hole 15; Oil hydraulic circuit by-pass flow path is: oil pocket 10---driven inner core internal oil passages 14---overflow hole 16---plunger internal oil passages 13, as shown in Figure 1 and Figure 2.
2, described solenoid valve 3 promotes plungers 4 and overcomes return spring 7 active forces and inwardly enter driven inner core 2 and put in place, and described relief hole 15 is sealed by the little axis hole of driven inner core 2 with the corresponding connection of driven inner core internal oil passages 14, described overflow hole 16.
Oil hydraulic circuit path is: bearing internal oil passages 17---bearing position oil circuit 11---and camshaft axle head internal oil passages 12---the large axis hole of driven inner core 2---plunger internal oil passages 13---relief hole 15---driven inner core internal oil passages 14---oil pocket 10, as shown in Figure 3, Figure 4.
Working procedure of the present invention:
When engine operation, the controlling rod of solenoid valve 3 is retracted, and under return spring 7 effects, plunger 4 moves to high order end (as shown in Figure 1), and the relief hole 15 on plunger 2 exposes driven inner core 2, and overflow hole 16 just communicates with driven inner core internal oil passages 14.Under pump function, engine lubrication machine oil enters camshaft 6 axle heads from bearing support 20, by the large axis hole of driven inner core 2, flow in the oil circuit of plunger 4, finally by the relief hole 15 on plunger 4, flow into oil sump, now, in oil pocket 10, there is no pressure lubrication oil, drive wheel 5 drives initiatively urceolus 1, initiatively urceolus 1 drives driven inner core 2 to rotate by internal tooth 8 and the external tooth 9 (minimum gap location) being in contact with one another, and realizes the normal operation of camshaft 6, as shown in Figure 2.
Under some predetermined rotating speed and load condition, solenoid valve 3 is by electronically controlled fuel injection system and igniting management system incentive, the controlling rod of solenoid valve 3 stretches out, promotion plunger 4 moves right and puts in place (as shown in Figure 3), relief hole 15 on plunger 4 enters in driven inner core 2 and communicates with driven inner core internal oil passages 14, and 16 of overflow holes are sealed by the little axis hole of driven inner core 2.Under pump function, engine lubrication machine oil enters camshaft 6 axle heads from bearing support 20, by driven inner core 2 macropores, flow in the oil circuit of plunger 4, by relief hole 15 and driven inner core internal oil passages 14, flow into oil pocket 10, in rotational direction promote forward external tooth 9, thereby make active urceolus 1 and driven inner core 2 relatively rotate several angle (being illustrated in figure 4 position, maximal clearance), be that drive wheel 5 relatively rotates several angle with camshaft 6, so the advance angle of intake valve increases, the angle that lags is corresponding to be reduced.
Control the pressure of lubricant oil, can control active urceolus 1 and driven inner core 2 angle in relative rotation, and realize electrodeless variable valve timing, regulate.
Claims (5)
1. electrodeless variable valve timing mechanism, it is characterized in that: comprise mechanical control section and hydraulic control part, described mechanical control section comprises the active urceolus (1) of coaxial package and driven inner core (2) and the plunger (4) being promoted by solenoid valve (3), described active urceolus (1) is coaxially connected with drive wheel (5), one end axis hole of described driven inner core (2) and camshaft (6) one axle heads are coaxially connected, described plunger (4) is coaxially snug fit at driven inner core (2) the other end axis hole, in driven inner core (2) axis hole between plunger (4) and camshaft (6), press-fit return spring (7), described active urceolus (1) passes through corresponding in plunger (4) position with driven inner core (2), external tooth (8, 9) transmission, in described, external tooth (8, 9) and driven inner core (2) upper circumference uniform distribution setting interior respectively at active urceolus (1), external tooth (9) circumferential size is less than internal tooth (8) circumferential size and the oil pocket (10) of between formation variable volume, the loop of described hydraulic control part comprises the bearing position oil circuit (11) of camshaft (6), the axle head internal oil passages (12) of camshaft, plunger internal oil passages (13) and corresponding to the radially driven inner core internal oil passages (14) of each oil pocket (10) circumference uniform distribution, on plunger (4), offer respectively the radially relief hole (15) of circumference uniform distribution and overflow hole (16) radially, described relief hole (15) and overflow hole (16) can be communicated with driven inner core internal oil passages (14) respectively.
2. electrodeless variable valve timing mechanism according to claim 1, it is characterized in that: described plunger (4) enters driven inner core (2) and puts in place, described overflow hole (16) sealing, described relief hole (15) is communicated with driven inner core internal oil passages (14), each oil pocket (10) oil-feed pressurize.
3. electrodeless variable valve timing mechanism according to claim 1, it is characterized in that: described plunger (4) exits driven inner core (2) and puts in place, described relief hole (15) exposes, described overflow hole (16) is communicated with driven inner core internal oil passages (14), each oil pocket (10) draining decompression.
4. according to the electrodeless variable valve timing mechanism described in any one in claim 1～3, it is characterized in that: bearing support (20) is installed the bearing position of described camshaft (6) and by seal ring (18) sealing attachment face, bearing support internal oil passages (17) is communicated with bearing position oil circuit (11).
5. according to the electrodeless variable valve timing mechanism described in any one in claim 1～3, it is characterized in that: described drive wheel (5) is biserial sprocket wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410180877.3A CN103953408B (en) | 2014-04-30 | 2014-04-30 | Electrodeless variable valve timing mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410180877.3A CN103953408B (en) | 2014-04-30 | 2014-04-30 | Electrodeless variable valve timing mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103953408A true CN103953408A (en) | 2014-07-30 |
| CN103953408B CN103953408B (en) | 2016-08-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410180877.3A Expired - Fee Related CN103953408B (en) | 2014-04-30 | 2014-04-30 | Electrodeless variable valve timing mechanism |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1629453A (en) * | 2003-12-16 | 2005-06-22 | 依纳-谢夫勒两合公司 | Internal combustion engine with hydraulic camshaft phasing device |
| CN1965149A (en) * | 2004-06-08 | 2007-05-16 | 谢夫勒两合公司 | Vane-type camshaft adjuster |
| CN1985070A (en) * | 2004-07-10 | 2007-06-20 | 谢夫勒两合公司 | Electrically driven camshaft adjuster |
| US20110220046A1 (en) * | 2010-03-09 | 2011-09-15 | Schwabische Huttenwerke Automotive Gmbh | Cam shaft phase setter comprising a control valve for hydraulically adjusting the phase position of a cam shaft |
| CN203822401U (en) * | 2014-04-30 | 2014-09-10 | 桂林电子科技大学 | Stepless variable gas distribution timing mechanism |
-
2014
- 2014-04-30 CN CN201410180877.3A patent/CN103953408B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1629453A (en) * | 2003-12-16 | 2005-06-22 | 依纳-谢夫勒两合公司 | Internal combustion engine with hydraulic camshaft phasing device |
| CN1965149A (en) * | 2004-06-08 | 2007-05-16 | 谢夫勒两合公司 | Vane-type camshaft adjuster |
| CN1985070A (en) * | 2004-07-10 | 2007-06-20 | 谢夫勒两合公司 | Electrically driven camshaft adjuster |
| US20110220046A1 (en) * | 2010-03-09 | 2011-09-15 | Schwabische Huttenwerke Automotive Gmbh | Cam shaft phase setter comprising a control valve for hydraulically adjusting the phase position of a cam shaft |
| CN203822401U (en) * | 2014-04-30 | 2014-09-10 | 桂林电子科技大学 | Stepless variable gas distribution timing mechanism |
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| Publication number | Publication date |
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| CN103953408B (en) | 2016-08-17 |
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Granted publication date: 20160817 |
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