CN221074394U - Internal combustion engine - Google Patents
Internal combustion engine Download PDFInfo
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- CN221074394U CN221074394U CN202322785678.2U CN202322785678U CN221074394U CN 221074394 U CN221074394 U CN 221074394U CN 202322785678 U CN202322785678 U CN 202322785678U CN 221074394 U CN221074394 U CN 221074394U
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- combustion engine
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 34
- 230000005540 biological transmission Effects 0.000 claims abstract description 34
- 230000001788 irregular Effects 0.000 claims description 2
- 230000007246 mechanism Effects 0.000 abstract description 29
- 230000033001 locomotion Effects 0.000 abstract description 18
- 238000007789 sealing Methods 0.000 abstract description 4
- 230000003993 interaction Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 12
- 238000005265 energy consumption Methods 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000010791 quenching Methods 0.000 description 2
- 230000000171 quenching effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005121 nitriding Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
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- Valve-Gear Or Valve Arrangements (AREA)
Abstract
The utility model discloses a valve mechanism of an internal combustion engine. The valve seat comprises a timing gear, a valve guide pipe, a valve seat, a transmission shaft which is distributed on a shaft body and provided with a disc-shaped object and a shifting fork corresponding to a cylinder in a specific phase, and a connecting part for connecting the valve. The valve is opened and closed by the relative movement between the axial bulge on the shifting fork on the transmission shaft and the groove on the connecting part, and then the sealing after the valve is closed is realized by the matching and interaction of the fan-shaped arc end face of the disk on the transmission shaft and the axial bulge at one end of the connecting part. The valve mechanism solves the problem that when the valve mechanism of the internal combustion engine runs at high speed, the valve is not closed yet and is opened by the cam rotating at high speed, and solves the resonance phenomenon generated by the valve spring and the energy loss caused by the valve spring.
Description
Technical field:
the present utility model relates to internal combustion engines, and more particularly to valve trains for internal combustion engines.
The background technology is as follows:
At present, a valve mechanism of a four-stroke internal combustion engine is composed of a valve driving group and a valve group, wherein the valve driving group is all parts from a timing gear to pushing a valve to act, the components of the valve driving group are different according to the form of the valve mechanism, the valve driving group has the function of driving a valve to open and close at fixed time, and the composition of the valve group is basically irrelevant to the form of the valve mechanism. When the valve mechanism works, the valve has three states, namely a valve opening process, a valve closing process and a valve keeping closing process; the valve opening process directly or indirectly drives the valve to open through the rotation of a cam on a cam shaft, and simultaneously compresses a valve spring; the valve closing process is that the valve drives the valve to close under the action of the tension of the valve spring; the valve keeps closed under the action of the pre-tension force of the valve spring. Because the forces born by the opening and closing of the valve come from the cam and the valve spring respectively, and the directions of the acting forces on the valve are opposite, perfect matching is difficult to realize when the acting forces are switched, and when the rotating speed of the internal combustion engine reaches a certain high, the phenomenon that the valve is not completely closed but is opened by the cam rotating at a high speed usually occurs, so that the valve is separated from the cam; when the working frequency of the valve spring is equal to or integral multiple of the natural vibration frequency, the valve spring can resonate, the valve timing is destroyed during resonance, and the valve can rebound and impact; in addition, the valve spring generates certain energy loss because the valve is opened to overcome the tension of the valve spring.
The utility model comprises the following steps:
The utility model aims to overcome the defects of the existing valve actuating mechanism of the internal combustion engine, combines the valve opening process and the valve closing process into a valve opening process through the improvement of the valve actuating mode of the valve actuating mechanism of the internal combustion engine, realizes the smooth direction conversion of the acting force on the valve, eliminates the separation phenomenon of a mechanism contact piece, eliminates the resonance of a valve spring and eliminates the energy consumption loss caused by the valve spring.
The technical scheme is as follows:
The utility model relates to a valve actuating mechanism of an internal combustion engine, which comprises a timing gear, a valve guide pipe and a valve seat, and is characterized in that: the device also comprises a transmission shaft which is distributed on the shaft body and provided with a disc-shaped object and a shifting fork corresponding to the air valve in a specific phase and a connecting part for connecting the air valve; the shifting fork is a support arm of the transmission shaft from inside to outside, the end of the support arm is provided with an axial bulge, the axial projection of the disk is in a sector shape, the central angle of the disk is beta, and the axial projection of the bulge is intersected with the axial projection of an angular bisector of the beta; one end of the connecting part is provided with an axial bulge, the other end of the connecting part is at least connected with one valve, the middle part of the connecting part is axially projected into an irregular fan shape, the central angle of the connecting part is eta, eta is more than or equal to 115 degrees and less than or equal to 145 degrees, the eta is opened towards the valve, and a groove is formed on the disk surface; the sum of said η and said β is equal to 360 degrees; the radial projection of the axis of the transmission shaft is perpendicularly intersected with the radial projection of the central line of the connecting part and the valve; when the transmission shaft rotates, the axial protrusions of the end heads of the support arms move relatively in the grooves in part phases, the axial protrusions are matched with the grooves in a clearance fit mode, and the fan-shaped arc end faces of the disk-shaped objects in other phases are matched with and interact with the axial protrusions at one end of the connecting part.
The beneficial effects are that:
The utility model is characterized in that the axial bulge on the shifting fork on the transmission shaft and the groove on the connecting part are adopted to make relative movement to drive the driven part formed by the connecting part and the valve to move up and down, so that the process from opening to closing of the valve is realized, and the circular arc end surface of the disk on the transmission shaft is matched with and interacted with the axial bulge at one end of the connecting part, so that the sealing after closing of the valve is realized; the valve spring is directly acted on the valve, so that the valve is effectively controlled in the working process, the problem that a contact piece is separated when the valve mechanism of the existing internal combustion engine works at a high speed is solved, and the phenomenon of valve spring resonance and energy consumption loss caused by the valve spring are eliminated.
1: Energy consumption of valve spring:
The conditions are known: full combustion of 1kg of gasoline releases 46000kj of heat.
Assume the condition: a traditional four-cylinder four-valve gasoline engine runs at a speed of two thousand revolutions per minute, the opening force of each valve is 600N, the valve stroke is 10mm, and the engine runs for one hour.
Valve spring energy consumption: valve number valve opening force stroke =1 hour valve number of operations per minute
Q (actual valve spring energy consumption) =60×2000/2×16×600×0.01=5760 (kj);
1L (935 petrol) =0.737 kg;
Q (1L-93 # gasoline) =46000×0.737= 33902 (kj);
Q (oil consumption of actual valve spring) =q (energy consumption of actual valve)/Q (1L-93 # gasoline)
＝5760/33902＝0.170(L)＝170(ml)；
2: Influence of resonance on valve train:
Because the valve spring exists in the valve mechanism of the existing internal combustion engine, the whole valve mechanism forms an elastic system, and the working frequency of the valve spring is overlapped with the self-vibration frequency thereof to generate resonance, so that the valve rebound impact is caused, and the normal operation of the internal combustion engine is influenced.
3: Impact of high rotational speed on valve train:
a: assuming that the rotational speed of an internal combustion engine is 8000 rpm;
b: assuming that the valve spring closes the valve for 0.02 seconds;
Because the camshaft rotational speed is half of the crankshaft rotational speed, 8000/2/60=200/3 (revolutions per second), so camshaft rotational time of one revolution is 3/200 seconds, if the valve is under the action of the valve spring tension, the valve will be closed inaccurately when the valve is closed for more than 15 thousandths of a second, even the normally open phenomenon of the intake valve and the exhaust valve occurs, and the normal working cycle of the internal combustion engine is destroyed.
Description of the drawings:
FIG. 1 is a schematic diagram of the present utility model;
FIG. 2 is a detail drawing of the present utility model;
FIG. 3 is an assembly view of an embodiment of the present utility model;
FIG. 4 is an exploded view of an embodiment of the present utility model;
FIG. 5 is an assembly view of other form 1 of the present utility model;
FIG. 6 is an exploded view of other form 1 of the present utility model;
FIG. 7 is an assembly view of other form 2 of the present utility model;
FIG. 8 is an exploded view of other form 2 of the present utility model;
FIG. 9 is an assembly view of other form 3 of the present utility model;
FIG. 10 is an exploded view of other form 3 of the present utility model;
FIG. 11 is a schematic illustration of a valve train thrust profile of the present utility model;
fig. 12 is a schematic view of the valve train pressure angle of the present utility model.
In the figure, a timing gear, a2 transmission shaft, a 2-1 disk sector disk arc end face, an axial cylindrical bulge (roller) on a 2-2 shifting fork, a 3 connecting part, a 3-1 connecting part top, a groove on the 3-2 connecting part, a 5 valve, a 6 key, a 7-shaft head lock nut, a 9 pin, a 10 valve guide pipe, an 11 valve seat, eta is a central angle corresponding to a groove theoretical profile, eta=/COD, beta is a central angle of the sector disk, beta= angle EOF, an A shifting fork, a B disk and a CD groove theoretical profile.
The specific embodiment is as follows:
In order to simplify the structure of the utility model, the disc (sector disc) on the transmission shaft and the shifting fork are overlapped into a whole, after being combined, the sector disc with a specific phase is distributed on the transmission shaft, and the axial cylindrical bulge is arranged on the angular bisector of the sector disc, so that the utility model is realized by utilizing the cylindrical bulge on the sector disc to drive the driven part.
As shown in fig. 1, 2, 3 and 4: the valve mechanism driving part of the internal combustion engine comprises a timing gear 1 and a transmission shaft 2, and the driven part comprises a connecting part 3 and a valve 5; the valve guide 10 and the valve seat 11 are mounted on the cylinder cover in an interference fit manner.
Timing gear: in the present embodiment, the timing gear 1 is not different from that used in the existing internal combustion engine.
A transmission shaft: after the fan-shaped disc on the transmission shaft 2 is combined with the shifting fork, an axial cylindrical bulge 2-2 is arranged on the angular bisector of the fan-shaped disc, the diameter of the axial cylindrical bulge is equal to the width of the groove 3-2 on the connecting part 3, and the central angle of the fan-shaped disc is beta, and beta= EOF.
A connecting part: as shown in fig. 2 and 4: the upper half part of the connecting part 3 is in a long strip shape, the lower half part is in a crescent shape, the axial projection of the connecting part 3 is in an inverted 'e' shape, an asymmetric structure is adopted, the connecting part is formed by combining two inverted 'e' shapes, the distance between the inverted 'e' shapes and the thickness of a fan-shaped disc on the transmission shaft 2 are equal, the bottom and the top of the connecting part are connected, the lower half part of the crescent shape is radially provided with a groove 3-2, the two grooves 3-2 are opposite and mirror images, the groove 3-2 is positioned in the connecting part 3, the theoretical profile CD of the groove is in a smooth curve, the central angle corresponding to the theoretical profile CD of the groove is eta, eta= is equal to the angle of COD, eta angle opening is downward, eta+beta = 360 DEG, eta is equal to or less than 145 DEG, the bottom of the connecting part 3 is provided with a hole in the vertical direction, the diameter of the hole is equal to the diameter of the valve rod, the lower surface of the top 3-1 of the connecting part can be a plane or a curved surface, the maximum distance from the lower surface to the transmission shaft is smaller than the radius of the fan-shaped disc.
The present embodiment is connected by the following manner, as shown in fig. 3: the timing gear 1 is connected with the transmission shaft 2 through a key 6, a key groove and a spindle head lock nut 7; as shown in fig. 4: the fan-shaped disc on the transmission shaft 2 is arranged in the connecting part 3, and the fan-shaped disc is in clearance fit with the connecting part 3; the hole at the bottom of the connecting part 3 is matched with the valve stem and is fixedly connected through a pin 9.
When the timing gear 1 drives the transmission shaft 2 to rotate, the fan-shaped disc arc end face 2-1 is matched with and interacts with the top 3-1 of the connecting part 3, the valve 5 is in a closed state, because the maximum distance from the lower surface of the top 3-1 of the connecting part 3 to the axis of the transmission shaft is smaller than the radius of the fan-shaped disc, the top 3-1 of the connecting part 3 is extruded by the fan-shaped disc arc end face 2-1, the top 3-1 of the connecting part elastically deforms to generate an acting force opposite to the opening direction of the valve 5, the opposite acting force causes the connecting part 3 and the valve 5 to generate a movement trend opposite to the opening direction of the valve 5, the valve 5 is tightly attached to the valve seat 11, the sealing after the valve 5 is closed is realized, the rotation angle of the transmission shaft 2 in the period is beta, and the valve 5 is in a closed state in the rotation angle; when the arc end face 2-1 of the fan-shaped disc is separated from the top 3-1 of the connecting part 3, the axial cylindrical bulge 2-2 on the fan-shaped disc enters the groove 3-2 at the lower half part of the connecting part 3, the bulge 2-2 moves in the groove 3-2, the bulge and the groove are matched to be clearance fit, the valve 5 and the connecting part 3 can only move along the central line of the valve guide pipe 10 due to the constraint of the valve guide pipe, the difference between the distance from the point on the theoretical profile CD of the groove to the axis of the transmission shaft and the turning radius OC is changed from small to large to small, when the transmission shaft 2 rotates, the valve 5 is gradually opened from the closed state to the maximum lift and then from the maximum lift to the closed state, the opening and closing process of the valve 5 is completed, at the moment, the corner of the transmission shaft 2 is eta, and eta+beta=360 DEG is carried out along with the rotation of the transmission shaft 2, and the next cycle is repeatedly carried out. [ note: Φ ( Angle of thrust motion )＝η/2 Φ'( Return motion angle ) =η/2
In the above embodiments, the valve train of the internal combustion engine is connected to one valve, and it may also be connected to two or more valves of the same type in the same cylinder by a connecting rod or other means.
In the above embodiment, the valve actuating mechanism of the internal combustion engine is that the axial protrusion at the top of the connecting part is extruded by the arc end face of the fan-shaped disc, and the axial protrusion at the top of the connecting part is elastically deformed, so that the valve is kept in a closed state due to the reaction force generated by the axial protrusion.
The valve mechanism of the internal combustion engine realizes light load operation during working, so the material can be subjected to surface quenching to 56-60 HRC by using 40Cr, or subjected to nitriding treatment to 60-67 HRC by using 38CrMoA1, and in the embodiment, the materials such as 20Cr, 20CrMn and the like are subjected to surface quenching to ensure that the hardness reaches 55-60 HRC, and the valve mechanism is also suitable.
The embodiment is characterized in that a shifting fork on a transmission shaft rotates, and the connecting part is driven to move up and down to drive a valve to open and close by the relative movement between the shifting fork and a groove on the connecting part; of course, other layout arrangements may be used in embodiments, as shown in fig. 5 and 6: the connecting part is arranged between the two fan-shaped discs, grooves matched with the axial cylindrical protrusions on the fan-shaped discs are formed in two sides of the lower part of the connecting part, and the arrangement is beneficial to reducing the quality of the connecting part and reducing the motion inertia; fig. 7 and 8 are the sector plate and the shifting fork on the transmission shaft respectively independent, and the layout is similar to that of fig. 5 and 6; fig. 9 and 10 are also independent of the fan-shaped disc and the fork on the transmission shaft, and are similar to fig. 7 and 8 in layout, except that the fork on the transmission shaft is inside the connecting part; in addition, as the structure is opposite to that of fig. 9 and 10, shifting forks are arranged at two sides of the connecting part, and a fan-shaped disc is arranged inside the connecting part.
The above embodiments and the following description of the valve train of the internal combustion engine have the structure that each unit adopts a double-shifting fork structure, so as to make the whole mechanism operate more stably, each unit can also adopt a single-shifting fork structure, the structure is simpler-! But the stability is inferior to the structure of the double fork.
The utility model relates to a valve actuating mechanism of an internal combustion engine, which belongs to the category of cam mechanisms and is a variation of the cam mechanisms, in addition, a mode of maintaining high auxiliary contact in the existing valve actuating mechanism of the internal combustion engine (valve opening and closing) is realized by adopting force locking, valve opening and closing stress is from a cam and a valve spring, a mode of maintaining high auxiliary contact in the valve actuating mechanism of the internal combustion engine (valve opening and closing) is realized by adopting form locking, and the force born by a valve is from a shifting fork; when the valve of the valve mechanism of the existing internal combustion engine is in a closed state, the sealing of the valve is acted by the pre-tension force of a valve spring, and the utility model is realized by matching the sector disc with a locking device, and is similar to a disc cam mechanism with force locking.
Regarding the selection of the motion rule of a driven piece in the valve actuating mechanism of the internal combustion engine, the motion rule of a valve in the existing valve actuating mechanism of the internal combustion engine generally adopts a five-time polynomial motion rule (the profile of a cam determines the motion rule of the valve), the five-time polynomial motion rule is characterized by being suitable for high-speed medium load, the valve spring directly acting on the valve is not arranged in the valve actuating mechanism of the internal combustion engine, the light-load operation is realized, the motion rule of the valve can be selected from a sine acceleration motion rule, the sine acceleration motion rule is characterized by being suitable for high-speed light load, the cam profile is improved by changing the valve motion rule, and the ventilation efficiency of the internal combustion engine is improved.
A push profile equation:
establishing a coordinate system by adopting a reverse method, and solving the coordinates of the high auxiliary contact point; as shown in fig. 11:
Base radius r b; a bias distance e; b 0 is a promotion starting point; b is any contact point of the high pair (roller center); o is a rotation center; s is the displacement of the driven member; the radius of the roller is r r; tan theta is the normal slope of the point B; h is the stroke.
BB’＝S A’B’＝S0 A'B＝S0-S
The coordinates of the point B are the coordinates of the center of the roller:
actual profile equation for the groove wall:
pressure angle: as shown in fig. 12:
lop=v/ω (p-point is the relative instant center) tanα＝(e+lop)/(S0-S)
Because: s 0 2+e2＝rb 2 so: tan alpha= (e+lop)/[ (r b 2-e2)1/2 -S) ]
A base circle radius;
Alpha < [ alpha ] (allowable pressure angle) pressure angle range (25-35 DEG)
S, a sine acceleration motion rule is required to be met;
Namely:
Or S meets the rule of five-time polynomial movement;
Namely:
The joint of the near-break and the pushing stroke and the joint of the return stroke and the near-break are required to be provided with buffer sections, and the joint of the pushing stroke and the return stroke is required to be ensured to be smooth and excessive. Cams were generated using Camtra plug-ins in the solidworks software.
Claims (3)
1. The utility model provides an internal-combustion engine valve train, it includes timing gear, valve guide, valve seat, its characterized in that: the device also comprises a transmission shaft which is distributed on the shaft body and provided with a disc-shaped object and a shifting fork corresponding to the air valve in a specific phase and a connecting part for connecting the air valve; the shifting fork is a support arm of the transmission shaft from inside to outside, the end of the support arm is provided with an axial bulge, the axial projection of the disk is a sector, and the central angle of the disk is beta; the axial projection of the bulge intersects the axial projection of the angular bisector of beta; one end of the connecting part is provided with an axial bulge, the other end of the connecting part is at least connected with one valve, the middle part of the connecting part is axially projected into an irregular fan shape, the central angle of the connecting part is eta, the eta is open towards the valve, and a groove is formed in the disk surface; the sum of said η and said β is equal to 360 degrees; the radial projection of the axis of the transmission shaft is perpendicularly intersected with the radial projection of the central line of the connecting part and the valve; when the transmission shaft rotates, the axial protrusions of the end heads of the support arms move relatively in the grooves in part phases, the axial protrusions are matched with the grooves in a clearance fit mode, and the fan-shaped arc end faces of the disk-shaped objects in other phases are matched with and interact with the axial protrusions at one end of the connecting part.
2. A valve train for an internal combustion engine according to claim 1, wherein: the eta is more than or equal to 115 degrees and less than or equal to 145 degrees.
3. A valve train for an internal combustion engine according to claim 1, wherein: the theoretical profile of the groove is a smooth curve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322785678.2U CN221074394U (en) | 2023-10-12 | 2023-10-12 | Internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322785678.2U CN221074394U (en) | 2023-10-12 | 2023-10-12 | Internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN221074394U true CN221074394U (en) | 2024-06-04 |
Family
ID=91273286
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322785678.2U Active CN221074394U (en) | 2023-10-12 | 2023-10-12 | Internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN221074394U (en) |
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2023
- 2023-10-12 CN CN202322785678.2U patent/CN221074394U/en active Active
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