CN2761849Y - Variable distributing phase mechanism of gasoline engine - Google Patents
Variable distributing phase mechanism of gasoline engine Download PDFInfo
- Publication number
- CN2761849Y CN2761849Y CN 200520001150 CN200520001150U CN2761849Y CN 2761849 Y CN2761849 Y CN 2761849Y CN 200520001150 CN200520001150 CN 200520001150 CN 200520001150 U CN200520001150 U CN 200520001150U CN 2761849 Y CN2761849 Y CN 2761849Y
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- camshaft
- centrifugal
- driving wheel
- variable valve
- valve timing
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Abstract
The utility model relates to a variable gas distributing phase mechanism for a gasoline engine. The utility model comprises a cam shaft provided with a plurality of cams; the cam shaft is also orderly provided with a driven disk and a drive wheel, wherein the driven disk is provided with convex columns, and the drive wheel is correspondingly provided with arc-shaped grooves; the convex columns are inserted into the arc-shaped grooves and slide in the arc-shaped grooves, so that the driven disk forms displacement relatively to the drive wheel. The outer side of the drive wheel is provided with two centrifugal blocks; the centrifugal blocks are respectively a sheet-shaped body, and each edge contour is an irregular curve; the centrifugal blocks are provided with positioning holes which correspondingly penetrate on fixed columns of the drive wheel; both ends of each centrifugal body are respectively connected head to tail through elastic elements; the centrifugal blocks are provided with slide grooves, and the convex columns on the driven disk are inserted into the slide grooves through the drive wheel and are capable of sliding in the slide grooves. The variable gas distributing phase mechanism provided by the utility model omits the existing complicated and expensive components and parts, such as an ECU, an electromagnetic valve, a plurality of sensors, etc. and has the advantages of simple integral mechanism structure, small part quantity, easy processing and low cost.
Description
Technical field
The utility model relates to a kind of petrol engine distribution device, and especially a kind of petrol engine variable valve timing device belongs to petrol engine manufacturing technology field.
Background technique
As shown in Figure 1, be regular gasoline engines distribution phase diagram.As can be known from Fig. 1, α is an intake advance angle, and β is that the angle is closed in exhaust late, and θ is that the angle is closed in air inlet late, and γ is an exhaust advance angle.
Port timing choose the performance requirement that is decided by motor, and must adapt with the engine air flue shape and size.Port timing all has very big influence to the ventilation quality of motor, pumping loss, charging efficiency, moment of torsion external characteristics, idle stability, noxious emission etc.Intake valve has the scavenging effect of bigger open area and air inlet during for the assurance top dead center, and intake valve should have a certain size intake advance angle; For making full use of the air-flow inertia of air inlet, intake valve should have a certain size air inlet to close the angle late; Exhaust valve has bigger aperture and less exhaust resistance in the exhaust stroke in order to make, and exhaust valve should have a certain size exhaust advance angle; For reducing restriction loss, make full use of air-flow inertia, exhaust valve should have a certain size exhaust to close the angle late; Under the prerequisite that guarantees the high engine speeds performance, waste gas flows backwards when avoiding low speed, improves low engine speed performance and idle stability, should select less valve overlap as far as possible; Here said valve overlap is that the angle sum is closed in intake advance angle and exhaust late.
Existing employing cam directly or to drive valve switching mode indirectly by rocking arm be the four stroke engine of distribution device, needs different port timings just can obtain optimum performance under its different operating mode, mainly refers to power and moment of torsion.During high speed when guaranteeing top dead center intake valve the scavenging effect of bigger open area and air inlet is arranged, intake valve needs a certain size intake advance angle to open, angle refers to crank angle herein, the inertia of mixed gas when making full use of air inlet, and intake valve will have the big air inlet of trying one's best to close the angle late; The inertia of waste gas when making full use of exhaust, exhaust valve will have a certain size exhaust to close the angle late, and valve overlap should be tried one's best greatly.One of key character of high power engine is exactly, adopt big valve overlap and big air inlet to close the angle late, because the time that each stroke of piston is spent during high speed is very short, and intake velocity can't reach the velocity of sound, so should make full use of air inlet inertia and exhaust inertia increases air inflow; During low speed, flow backwards for preventing mixed gas, will suitably reduce air inlet during with respect to high speed and close the angle late, valve overlap should be not excessive yet; And rotating speed motor excessive when valve overlap can cause that waste gas flows backwards when extremely low, but real engine this phenomenon can not occur, because its engine idle is not low concerning the Large-power High-Speed motor, generally be about 1000r/min, piston is finished a stroke and is only needed 1/8th seconds.Certainly, the excessive and air inlet of valve overlap closes late that the angle is excessive all can to make the low engine speed degradation.In sum, when satisfying Under Different Work Condition of Engine, to the different demands of port timing, its distribution part should adopt variable valve timing mechanism.
Use more variable valve timing mechanism mainly to realize the change of port timing now by electronically controlled hydraulic mechanism, be some rotating speeds, oil pressure, temperature transducer mainly by information acquisition system, information processing is ECU, control and actuator are compositions such as solenoid valve and hydraulic actuator, complex structure, cost is very high, this type systematic only uses on some less limousines, motor vehicular engine, is difficult to spread on most of economy cars, the motor vehicular engine and uses.
The model utility content
The purpose of this utility model is at the deficiencies in the prior art, a kind of petrol engine variable valve timing device is provided, press the height of engine crankshaft rotating speed, by intake cam or exhaust cam are rotated to an angle separately, or with the camshaft integral body change port timing that rotates to an angle, when satisfying high engine speeds with low speed to the different demands of port timing.
For achieving the above object, the utility model provides a kind of petrol engine variable valve timing device, it comprises a camshaft, this camshaft is provided with a plurality of cams, also be provided with driven disc and driving wheel on camshaft in turn, driven disc is provided with projection, and correspondence offers curve bath on the driving wheel, this projection inserts curve bath and can slide in curve bath, makes driven disc can produce displacement with respect to driving wheel; The outside of driving wheel is provided with two centrifugal, centrifugal is laminar body, its edge contour is an irregular curve, offer positioning hole on centrifugal, correspondence is located on the fixing column of driving wheel, two centrifugal two ends respectively by elastic element each other head and the tail connect, offer sliding-groove on centrifugal, the projection on the driven disc inserts sliding-groove by driving wheel and can slide in sliding-groove.
Described cam all is fixed on the camshaft, makes camshaft with respect to the whole rotation of driving wheel; Simultaneously, all right partial fixing of described cam is on camshaft, and part makes this free cam rotate with respect to driving wheel for being set in the free cam on the camshaft.One side of driven disc is convexly equipped with first round ring boss, in a described driving wheel side relative with driven disc, correspondence convexes with second round ring boss, first round ring boss and second round ring boss are fitted mutually to increase the area of contact of driving wheel and driven disc, the reliability of part stability of rotation and transmission of power when having improved the two generation relative movement.Centrifugal two laminar body that are mutually symmetrical for exterior contour, its outer wheels profile is a smoothed curve.In order to prevent to be arranged on each parts generation axial float on the camshaft, the camshaft in the described driving wheel outside is provided with limit stoper, and this limit stoper is lock washer and the locking nut that is installed in the camshaft end.Be used for two centrifugal two ends respectively each other the elastic element that connects of head and the tail be the pretension return spring.Stable in order to connect, be connected for the pawl type between the surface of contact of driven disc and free cam.In addition, between limit stoper, driving wheel, driven disc and the camshaft, also all be provided with packing ring each other in twos between the bonding surfaces.
In sum, the petrol engine variable valve timing device that the utility model provides, wherein centrifugal effect is equivalent to the crankshaft rotational speed sensor of available engine, this centrifugal is the significant components that changes the actuator of port timing, whole variable valve timing mechanism has saved ECU, solenoid valve and a plurality of sensor, makes that whole mechanism structure is simple, amount of parts is few and easy processing, with low cost.
Below in conjunction with the drawings and specific embodiments the technical solution of the utility model is described in detail.
Description of drawings
Fig. 1 is a regular gasoline engines distribution phase diagram;
Fig. 2 is that originally it uses the petrol engine variable valve timing device structure partial generalized section of new embodiment one;
Fig. 3 is the utility model embodiment two a petrol engine variable valve timing device structure partial generalized section;
Fig. 4 movement position schematic representation of centrifugal when being the utility model time of engine low speed;
Centrifugal movement position schematic representation when Fig. 5 turns round for the utility model high engine speeds.
Embodiment
Embodiment one
As shown in Figure 2, be the utility model embodiment one petrol engine variable valve timing device structure partial generalized section.As can be known from Fig. 2, the utility model provides a kind of petrol engine variable valve timing device, it comprises a camshaft 31, this camshaft 31 is provided with a plurality of cams 1 and 3, also be provided with driven disc 2 and driving wheel 4 on camshaft 31 in turn, driven disc 2 is provided with projection 21, and correspondence offers curve bath 42 on the driving wheel 4, this projection 21 inserts curve bath 42 and can slide in curve bath 42, makes driven disc 2 can produce displacement with respect to driving wheel 4.
In conjunction with Fig. 4, shown in Figure 5, centrifugal movement position schematic representation when being respectively the utility model low engine speed and running up.From Fig. 4, Fig. 5 as can be known, the outside of driving wheel 4 is provided with two centrifugal 5, centrifugal 5 is laminar body, its edge contour is an irregular curve, offer positioning hole 51 on centrifugal 5, correspondence is located on the fixing column 41 of driving wheel 4, and two centrifugal 5 two ends are respectively by elastic element 6 head and the tail connection each other, offer sliding-groove 52 on centrifugal 5, the projection 21 on the driven disc 2 inserts sliding-groove 52 by driving wheel and can slide in sliding-groove 52.
As shown in Figure 2, cam 1 and 3 all is fixed on the camshaft 31, makes camshaft 31 with respect to driving wheel 4 whole rotations.One side of driven disc 2 is convexly equipped with first round ring boss 22, in the relative side of driving wheel 4 and driven disc 2, correspondence convexes with second round ring boss 43, first round ring boss 22 and second round ring boss 43 are fitted mutually to increase the area of contact of driving wheel 4 and driven disc 2, the reliability of part stability of rotation and transmission of power when having improved the two generation relative movement.Centrifugal 5 two laminar body that are mutually symmetrical for exterior contour, its outer wheels profile is a smoothed curve.In order to prevent to be arranged on each parts generation axial float on the camshaft 31, the camshaft 31 in driving wheel 4 outsides is provided with limit stoper 32, and this limit stoper 32 is for being installed in the lock washer and the locking nut of camshaft 31 ends.Be used for that the elastic element 6 that connects is from beginning to end each other distinguished at two centrifugal two ends and be the pretension return spring.In addition, between limit stoper 32, driving wheel 4, driven disc 2 and the camshaft 31, also all be provided with packing ring 7 each other in twos between the bonding surfaces.
In conjunction with Fig. 2, Fig. 4 and Fig. 5 as can be known, the distribution cam axle 31 of this variable valve timing mechanism is not directly driven by driving wheel 4, but drive the driven disc 2 that links with spline Connecting format and camshaft by the rotation of centrifugal 5 on the driving wheel 4 a certain cylindrical fixing column 41 on driving wheel, and then rotate by driven disc 2 drive cam shaft 31 again.Self parallel axes of the axis of the running shaft on the driving wheel 4 and driving wheel 4 or camshaft, centrifugal 5 can only be around the rotation of this fixing column 41 running shafts and can not be along moving on its axial direction, have sliding-groove and curve bath on centrifugal 5 and the driving wheel 4, two projections on the driven disc all pass sliding-groove and the curve bath on centrifugal 5 and the driving wheel 4; Two pretension return springs are arranged, and Placement is as figure; Driven disc 2, driving wheel 4 are spacing by limit stoper 32 along the play of the axial direction of camshaft 3, between camshaft 3, driven disc 2, driving wheel 4, pad is housed, camshaft 3, packing ring, driven disc 2, driving wheel 4 all have certain interval, so that the rotation of 3 of driving wheels 4, driven disc 2, camshaft can be flexible.When the rotating speed of camshaft is lower than a certain critical value, because the centrifugal moment (centrifugal force) that " centrifugal " produces at first will overcome the resistance torque of pre-fastening moment (pretightening force) that " pretension return spring " produce and distribution device generation hereinafter to be referred as " distribution resisting moment ", so no relative rotary motion is relative static between the two between camshaft and the driving wheel, the engines distribution phase place remains unchanged, and centrifugal 5 state A as shown in Figure 4.When the rotating speed of camshaft is higher than a certain critical value, because the centrifugal moment (centrifugal force) that " centrifugal " produces is enough big, its a part of moment is used to overcome the pre-fastening moment (pretightening force) that " pretension return spring " produces, remaining centrifugal moment is used to overcome the distribution resisting moment, and (driven disc is connected with the spline form with camshaft to drive driven disc, all the time there is not relative movement between the two), and then rotate to an angle with respect to driving wheel clockwise (counterclockwise) by the driven disc drive cam shaft again or the projection on driven disc to arrive driving wheel circular arc movement slots end be that driven disc can't be with respect to driving wheel rotation back (top of driving wheel circular arc movement slots and the terminal position-limiting action that rises), camshaft keeps no relative movement still and between the driving wheel, and rotating together, thereby the change of the engines distribution phase place that realizes, centrifugal 5 state B as shown in Figure 5.
Embodiment two
As shown in Figure 3, be the utility model embodiment two petrol engine variable valve timing device structure partial generalized section.As can be known from Fig. 3, cam can also make this free cam 1 ' with respect to driving wheel 4 rotations for being set in the free cam 1 ' on the camshaft 31.Stable in order to connect, be connected for the pawl type between the surface of contact of driven disc 2 and free cam 1 '.Present embodiment and embodiment's one difference is that also therefore the end of camshaft 31 and driving wheel 4, do not need to install the limit stoper that is used to prevent the component axial float among the embodiment one herein by being welded together.
The other technologies feature of present embodiment is identical with embodiment one, and concrete technological scheme sees also embodiment one, does not repeat them here.
Need to prove at last, above embodiment is only unrestricted in order to the explanation the technical solution of the utility model, although the utility model is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement the technical solution of the utility model, and not breaking away from the spirit and scope of technical solutions of the utility model, it all should be encompassed in the middle of the claim scope of the present utility model.
Claims (10)
1, a kind of petrol engine variable valve timing device, it comprises a camshaft, this camshaft is provided with a plurality of cams, it is characterized in that: on camshaft, also be provided with driven disc and driving wheel in turn, driven disc is provided with projection, correspondence offers curve bath on the driving wheel, and this projection inserts curve bath and slides in curve bath; The outside of driving wheel is provided with two centrifugal, centrifugal is laminar body, its edge contour is an irregular curve, offer positioning hole on centrifugal, correspondence is located on the fixing column of driving wheel, two centrifugal two ends respectively by elastic element each other head and the tail connect, offer sliding-groove on centrifugal, the projection on the driven disc inserts sliding-groove by driving wheel and slides in sliding-groove.
2, petrol engine variable valve timing device according to claim 1 is characterized in that: described cam all is fixed on the camshaft.
3, petrol engine variable valve timing device according to claim 1 is characterized in that: described cam portion is fixed on the camshaft, and part is for being set in the free cam on the camshaft.
4, petrol engine variable valve timing device according to claim 3 is characterized in that: be connected for the pawl type between the surface of contact of described driven disc and free cam.
5, according to claim 1 or 2 or 3 or 4 described petrol engine variable valve timing devices, it is characterized in that: a side of described driven disc is convexly equipped with first round ring boss, in a described driving wheel side relative with driven disc, correspondence convexes with second round ring boss, and first round ring boss and second round ring boss are fitted mutually.
6, according to claim 1 or 2 or 3 or 4 described petrol engine variable valve timing devices, it is characterized in that: described centrifugal two laminar body that are mutually symmetrical for exterior contour, its outer wheels profile is a smoothed curve.
7, according to claim 1 or 2 or 3 or 4 described petrol engine variable valve timing devices, it is characterized in that: the camshaft in the described driving wheel outside is provided with the limit stoper that is used to prevent to be arranged on each parts generation axial float on the camshaft.
8, according to the described petrol engine variable valve timing device of claim 7, it is characterized in that: described limit stoper is lock washer and the locking nut that is installed in the camshaft end.
9, petrol engine variable valve timing device according to claim 7 is characterized in that: between described limit stoper, driving wheel, driven disc and the camshaft, all be provided with packing ring each other in twos between the bonding surfaces.
10, according to claim 1 or 2 or 3 or 4 described petrol engine variable valve timing devices, it is characterized in that: described elastic element is the pretension return spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520001150 CN2761849Y (en) | 2005-01-19 | 2005-01-19 | Variable distributing phase mechanism of gasoline engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520001150 CN2761849Y (en) | 2005-01-19 | 2005-01-19 | Variable distributing phase mechanism of gasoline engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2761849Y true CN2761849Y (en) | 2006-03-01 |
Family
ID=36094977
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520001150 Expired - Lifetime CN2761849Y (en) | 2005-01-19 | 2005-01-19 | Variable distributing phase mechanism of gasoline engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2761849Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1325771C (en) * | 2005-01-19 | 2007-07-11 | 重庆宗申技术开发研究有限公司 | Petrol engine variable valve timing device |
-
2005
- 2005-01-19 CN CN 200520001150 patent/CN2761849Y/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1325771C (en) * | 2005-01-19 | 2007-07-11 | 重庆宗申技术开发研究有限公司 | Petrol engine variable valve timing device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Effective date of abandoning: 20050119 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |