TWI693337B - Engine valve actuation mechanism - Google Patents

Abstract

An engine valve actuation mechanism, which can be installed on a cylinder head of the engine, mainly includes a drive shaft, a cam assembly, a driven assembly and a valve assembly; the drive shaft can be pivotally pivoted On the cylinder head, to link the cam assembly, and the driven assembly by the cam assembly, and then the valve assembly by the driven assembly, wherein the driven assembly is limited to a first Linear reciprocating motion between the position and a second position. In the first position, the intake valve or exhaust valve of the valve assembly can be linked to close the opposite intake or exhaust ports on the cylinder head. In the second position, the intake or exhaust valves are linked to open the opposite intake or exhaust ports. The valve actuation mechanism can directly pull to close or push to open the intake valve and exhaust valve. Therefore, it can effectively avoid time delay and excessive power loss, so as to achieve better results for intake and exhaust, and then improve Engine power output efficiency.

Description

Engine valve actuation mechanism

The invention relates to a valve actuation structure of an engine, in particular to a valve actuation mechanism that can be installed on a reciprocating internal combustion engine.

As we all know, a typical four-stroke reciprocating internal combustion engine engine generally includes a cylinder body and a cylinder head mounted on the cylinder body, and is equipped with a cooling system and a combustion system; the cylinder body is provided with a cylinder, a connecting rod, a piston, Crankshaft and other components; the cylinder head is provided with components such as an intake valve and an exhaust valve. The working principle of the engine is usually divided into the actuating strokes of four pistons of suction, compression, combustion and exhaust, and it is completed after the piston is up and down twice.

The top of the cylinder of most engines, also known as the cylinder head, is usually provided with two holes, an intake port and an exhaust port, respectively, and is provided with two valves for opening and closing the intake port The air port and exhaust port allow air or mixed fuel gas to enter the cylinder when the inlet valve opens, and allow the burned gas, that is, exhaust gas, to be discharged from the cylinder when the exhaust valve opens. The intake valve and the exhaust valve are closed for most of the time and only open during the intake and exhaust strokes.

The traditional intake valve or exhaust valve is mostly driven by a camshaft, which is synchronously driven by a crankshaft through a timing belt or chain. Generally, when the crankshaft rotates once, the camshaft only rotates half a turn. The camshaft usually drives the intake valve and the exhaust valve through a spring-type valve mechanism, that is, the camshaft pushes the intake valve or exhaust valve through the cam on it to open the intake port Or the exhaust port, but a compression spring will be compressed synchronously during the push-down process. Therefore, when the amount of down pressure of the cam disappears, the intake valve and exhaust valve can be closed by the elastic restoring force of the compression spring The air inlet and the air outlet. The disadvantage is that as the engine speed increases, it will gradually approach and exceed the limit of the rebound speed of the compression spring, so that the valve cannot be completely closed before the piston reaches the top dead center, and causes the following problems: first, the piston may Hit the valve that was not closed yet. Second, because the valve has not yet returned to the valve seat without fully closing the intake port, the upward compression stroke of the piston will push the mixed oil and gas out of the combustion chamber, resulting in a reduction in the engine compression ratio, which is insufficient. The situation may cause power loss and may also cause damage to the valve.

Traditionally, the elastic strength of the spring is used to solve the problem that the valve cannot be closed quickly, but it also causes the camshaft to apply more thrust to press the actuator to open the intake port or exhaust port, not only the timing belt or chain The rotation resistance becomes larger, and more engine output power is consumed to rotate the camshaft, but it still cannot ensure that the above problems are effectively solved. Increased resistance or friction will also cause the temperature of the moving parts to increase and wear. Exacerbated.

The invention provides an engine valve actuation mechanism that can be installed on a cylinder head of the engine, and the cylinder head has at least one intake valve seat and at least one exhaust valve seat, the intake valve The seat is formed with an intake port and an intake channel communicating with the intake port, the exhaust valve seat is formed with an exhaust port and an exhaust channel communicating with the exhaust port; the valve actuation mechanism Including: a drive shaft, which can be pivotally pivoted on the cylinder head; a cam assembly, including a first cam and a second cam, which can be fixed on the drive shaft; a driven assembly , Including a first follower and a second follower, can be driven by the first cam and the second cam, respectively, and are restricted to linear reciprocating motion between a first position and a second position ; FAW The assembly, including at least one intake valve and at least one exhaust valve, can be respectively installed on the intake valve seat and the exhaust valve seat, and each has a rod portion, and one extends from one end of the rod portion Valve part, the rod part is respectively connected to the opposite first follower and the second follower, the valve part can open or close the opposite inlet and exhaust ports respectively; when the first When a follower and a second follower are respectively displaced to the first position, the opposite intake and exhaust valves can be respectively linked to close the opposite intake and exhaust ports; when the first When the follower and the second follower are respectively displaced to the second position, the opposite intake and exhaust valves can be respectively linked to open the opposite intake and exhaust ports.

The steam valve actuating mechanism provided by the present invention can be directly pulled by the cam assembly through the driven assembly to close or push to open the intake valve and exhaust valve of the steam valve assembly, therefore, time delay can be effectively avoided , And the phenomenon of excessive power loss, so that the intake and exhaust achieve better results, and thus improve the power output efficiency of the engine.

1: Steam valve actuation mechanism

1a: Steam valve actuation mechanism

10: Drive shaft

20: Cam assembly

21: First cam

22: Second cam

23: cam slot

30: driven component

31: First follower

32: Second follower

33: Rotating components

331: Rotating parts

332: Mandrel

34: Shaft seat

341: The first wall

342: Second wall

343: Shaft hole

35: Lug

351: Piercing

36: connecting rod

40: Valve assembly

401: top nut

402: Press nut

41: Intake valve

42: Exhaust valve

43: Rod

430: buckle

431: put out the end

432: Unpenetrated part

44: Valve

45: First fixed ring sleeve

451: Spring positioning part

452: bottom wall

46: Second fixed ring sleeve

47: Positioning pin

50: Guide slide assembly

51: Guide slider

511: limit protrusion

52: Guide groove

60: The first elastic buffer

70: Elastic top support

80: second elastic buffer

100: spring assembly

101: First tension spring

102: Second extension spring

103: one end

104: the other end

200: Push tube assembly

201: The first push tube

202: The second push tube

203: one end

204: the other end

9: cylinder head

9a: Base part

9b: Wall part

91: Intake valve seat

911: Air intake

912: Intake passage

913: top wall surface

914: Rod penetration hole

92: Exhaust valve seat

921: Exhaust

922: Exhaust channel

923: Top wall surface

924: Rod penetration hole

93: accommodation space

94: positioning seat

941: Spring groove

942: Limit wall

P1: first position

P2: second position

d1: distance

d2: distance

S1: first gap

S2: Second gap

S3: third gap

S4: Fourth gap

1 is a perspective external view of an assembled state of a valve actuation mechanism mounted on a cylinder head according to a first embodiment of the present invention; FIG. 2 is another perspective external view of an assembled state of a valve actuation mechanism mounted on a cylinder head according to a first embodiment of the present invention Figure 3 is a perspective exploded view of the valve actuation mechanism and cylinder head of the first embodiment of the invention; Figure 4 is a schematic perspective view of the cylinder head of the first embodiment of the invention; Figure 5 is a first embodiment of the invention Figure 6 is a partial perspective cross-sectional schematic view of the cylinder head; Axial perspective sectional view of the drive shaft; FIG. 7 is a sectional view along the axial side of the intake valve in an assembled state in which the valve actuation mechanism of the first embodiment of the present invention is mounted on the cylinder head; The assembled embodiment of the valve actuation mechanism installed in the cylinder head is along the axial side sectional view of the exhaust valve; FIG. 9 is a partially enlarged schematic view of FIG. 7 of the present invention; FIG. 10 is a partially enlarged view of FIG. 8 of the present invention FIG. 11 is a perspective external view of an assembled state of a valve actuation mechanism mounted on a cylinder head according to a second embodiment of the invention; FIG. 12 is another assembled state of a valve actuation mechanism mounted on a cylinder head according to a second embodiment of the invention Fig. 13 is an exploded perspective view of the valve actuation mechanism and the cylinder head of the second embodiment of the invention; Fig. 14 is a view along the assembled state of the valve actuation mechanism of the second embodiment of the invention installed in the cylinder head Axial side sectional view of the intake valve; FIG. 15 is an axial side sectional view of the exhaust valve in the assembled state in which the valve actuation mechanism of the second embodiment of the present invention is mounted on the cylinder head.

As shown in FIGS. 1 to 3, the present invention provides a first embodiment of an engine valve actuation mechanism. The valve actuation mechanism 1 can be installed on a cylinder head 9 of the engine, and the cylinder head 9 has at least An intake valve seat 91 and at least one exhaust valve seat 92, as shown in FIGS. 4 and 5, this embodiment is provided with two intake valve seats 91 and two exhaust valve seats 92, and the Intake valve seat 91 various shapes An intake port 911 is formed, and at the same time, the intake valve seat 91 is provided with an intake passage 912 to communicate with the intake port 911; the exhaust valve seats 92 are each formed with an exhaust port 921, and at the same time, The exhaust valve seat 92 is provided with an exhaust passage 922 communicating with the exhaust port 921; the valve actuating mechanism 1 includes a driving shaft 10, a cam assembly 20, a driven assembly 30 and a valve assembly 40, wherein: the driving shaft 10, as shown in FIGS. 3 and 6, is pivotably pivotally connected to the cylinder head 9. The cylinder head 9 of this embodiment has a base portion 9a and two wall portions 9b extending upward from the base portion 9a; the intake valve seat 91 and the exhaust valve seat 92 are formed in the The base part 9a, and the air inlet 911 and the exhaust port 921 are formed on the bottom wall surface of the base part 9a, and the air intake channel 912 and the exhaust channel 922 are formed inside the base part 9a; An accommodating space 93 is defined between the wall portions 9b; the drive shaft 10 is accommodated in the accommodating space 93, and the two ends are respectively pivotally connected to the wall portions 9b.

The cam assembly 20 includes a first cam 21 and a second cam 22. The first cam 21 and the second cam 22 are fixedly connected to the drive shaft 10 at appropriate intervals. In this embodiment, it can be clearly seen that the cam assembly 20 is located in the accommodating space 93.

As shown in FIGS. 7 and 8, the driven assembly 30 includes a first driven member 31 and a second driven member 32, which can be driven by the first cam 21 and the second cam 22, respectively. It is restricted to reciprocate linearly between a first position P1 and a second position P2. It can be clearly seen from FIG. 7 that the first follower 31 is located at the first position P1, and this position is also the top dead center of the upward and downward displacement of the first follower 31. It can be clearly seen from FIG. 8 that the second follower 32 is located at the second position P2, which is also the bottom dead center of the upward and downward displacement of the second follower 32.

The steam valve assembly 40, as shown in FIGS. 3, 7 and 8, includes at least one inlet valve 41 And at least one exhaust valve 42, which can be respectively installed on the intake valve seat 2a and the exhaust valve seat 2b, and each has a rod portion 43 and a valve portion extending from one end of the rod portion 43 44. The rod portion 43 is connected to the opposing first follower 31 and the second follower 32 respectively. The valve portion 44 can respectively open or close the opposing intake port 911 and exhaust port 921. According to this, when the first follower 31 and the second follower 32 are respectively displaced to the first position P1, the opposing inlet valve 41 and the exhaust valve 42 can be respectively linked to close the opposing inlet The air port 911 and the exhaust port 921; when the first follower 31 and the second follower 32 are respectively moved to the second position P2, the respective inlet valve 41 and exhaust valve can be linked respectively 42 Open the opposing air intake port 911 and exhaust port 921. In this embodiment, a total of two intake valves 41 are installed on the two intake valve seats 91, and two exhaust valves 42 are installed on the exhaust valve seats 92, respectively.

In this embodiment, the first cam 21 and the second cam 22 are both grooved cams, each of which is formed with a cam groove 23, as shown in FIGS. 3, 7 and 8; the driven assembly 30 further includes Two rotating components 33 are respectively installed and fixed on the first follower 31 and the second follower 32. The rotating component 33 includes a rotating member 331, which rotatably accommodates the first The cam groove 23 of the cam 21 and the cam groove 23 of the second cam 22 can interlock the first follower 31 and the second follower with the rotation of the first cam 21 and the second cam 22 Piece 32.

In other words, since the first follower 31 and the second follower 32 are restricted to linear movement only up and down, when the first cam 21 and the second cam 22 follow the drive shaft 10 When rotating, you can use the non-circular cam groove 23 on the track, through the rotating member 331 to drive the opposing first follower 31 and the second follower 32 along the linear trajectory up and down For sliding displacement, the upper dead point of the upper and lower sliding displacement is the first position P1, and the lower dead point is the second position P2.

In this embodiment, the rotating assembly 33 further includes a mandrel 332, as shown in FIGS. 6-8, one end of which is fixed to the first follower 31 or the second follower 32, and the other end is The rotating members 331 are pivotally connected to each other, so that the rotating members 331 can rotate relative to the mandrel 332 while moving in the relative cam grooves 23, so that the rotating members 331 and the cam grooves 23 can be reduced from each other The frictional resistance generated during the relative movement further makes the cam assembly 20 and the driven assembly 30 actuate more smoothly.

It is easily imagined that the rotating member 331 can be a bearing, such as a common ball bearing, needle bearing, self-lubricating bearing, etc.

In this embodiment, the valve actuation mechanism 1 further includes a second guide slide assembly 50, as shown in FIGS. 3, 7 and 8; the guide slide assemblies 50 each include a second guide slider 51 and are disposed at a relative interval from each other On the cylinder head 9, a guide groove 52 can be formed between each other, so that the first follower 31 and the second follower 32 can be restricted to linearly reciprocate in the guide groove 52. The guide sliders 51 of the guide slide assemblies 50 of this embodiment are respectively locked to the inner wall surfaces of the opposite wall portions 9b of the cylinder head 9, but not limited to this, the wall portions can also be directly The inner wall surface of 9b is integrally formed.

In this embodiment, a limiting protrusion 511 protrudes from the inner side of the top end of the guide slider 51 of each guide assembly 50 to displace the first follower 31 and the second follower 32 to the In the first position P1, the top end of the first position P1 can be pressed by the relative limiting protrusions 511 to limit its continued upward displacement, the purpose is to reduce or avoid the first follower 31 and the second follower 32 and other members move to the first position P1 in the direction of the inertial force generated is transmitted to the rotating member 331, and damage to the rotating member 331 or the mandrel 332, etc., especially Damage caused by the collision between the rotating member 331 and each of the opposing cam grooves 23 is caused.

Obviously, the first follower 31 and the second follower 32 are displaced upward to the The structure that can be limited at a position P1 can have various implementation forms, and is not limited to the limiting structure formed between the above-mentioned limiting protrusions 511 and the opposing parts of each follower. For example, using the guide slider 51 and A concave-convex structure or a sliding-in structure with each other can also be provided between the followers, and the same limiting effect can also be achieved. These embodiments should be included in the technical scope of the present invention.

In this embodiment, the valve actuation mechanism 1 further includes two first elastic buffer members 60, as shown in FIGS. 3 and 6, which are fixed to the cylinder head 9 and are respectively connected to the first follower members 31 and the second follower 32 are opposed to each other, and when the first follower 31 and the second follower 32 move toward the second position P2, the first follower 31 is opposed The second follower 32 elastically resists the compression, thereby providing the elastic buffering effect required by the first follower 31 and the second follower 32 during the actuation process.

In this embodiment, the cylinder head 9 has two positioning seats 94, and each positioning seat 94 has a spring receiving groove 941, as shown in FIGS. 3 and 6; the first elastic buffer member 60 is a compression One end of the spring is accommodated and positioned in the spring accommodating groove 941, and the other end is provided for the first follower 31 and the second follower 32 to oppose each other. The positioning seat 94 of this embodiment is assembled and locked on the inner wall surface of each wall portion 9b of the cylinder head 9, but not limited to this, it may also be integrally formed from the inner wall surface of each wall portion 9b.

In this embodiment, when the first follower 31 and the second follower 32 are located at the first position P1, they are separated from the opposite end of the opposing first elastic buffer 60 by a distance d1, such as As shown in FIG. 7, the first elastic cushioning member 60 produces an elastic cushioning effect only during the final stroke of the first follower 31 and the second follower 32 moving in the direction of the second position P2, This means that the first elastic buffer 60 will not affect the first follower 31 and most of the strokes before the last stroke of the first follower 31 and the second follower 32. Displacement of the second follower 32 Sliding generates any resistance, and therefore, it can be ensured that the power from the drive shaft 10 will not suffer too much loss.

In this embodiment, a limiting wall 942 is further formed on the top of the positioning seat 94 to displace the first follower 31 and the second follower 32 to the second position P2, except for the elastic compression In addition to the first elastic buffer member 60, the bottom end of the first elastic buffer member 60 can be pressed against the limiting position by the relative limiting walls 942 to limit its continued downward displacement. The purpose is to reduce or avoid An inertial force generated when a member such as a follower 31 and a second follower 32 moves in the direction of the second position P2 is transmitted to the rotating member 331, which causes the rotating member 331, the mandrel 332, etc. Damage, especially damage caused by the collision between the rotating member 331 and the opposing cam grooves 23.

Similarly, the structure that can be limited when the first follower 31 and the second follower 32 are moved down to the second position P2 can have various implementation forms, and is not limited to the above-mentioned limiting wall 942 and each The limit structure formed between the relative parts of the follower, for example, the positioning seat 94 and each follower can be provided with a concave-convex structure or a mutual inset sliding structure, etc., and the same limit effect can also be achieved. It is included in the technical scope of the present invention.

In this embodiment, each of the first follower 31 and the second follower 32 is provided with a shaft seat 34, as shown in FIGS. 7 to 10, each of the shaft seats 34 has a first seat wall 341 With respect to the first cam 21 and the second cam 32, respectively, and each having a second seat wall 342 with respect to the intake valve seat 2a or the exhaust valve seat 2b, and on each shaft seat 34 A shaft hole 343 is formed between the first seat wall 341 and the second seat wall 342 respectively, so that the free ends of the rod portions 43 of the inlet valve 41 and the exhaust valve 42 can protrude therethrough. The steam valve assembly 40 further includes at least two first fixed ring sleeves 45 and at least two second fixed ring sleeves 46, and the first fixed ring sleeves 45 are respectively sleeved and connected to the inlet valve 41 and the exhaust valve 42 The rod portion 43 passes through the end 431 and is opposed to the first seat wall 341; the second solid The fixed ring sleeve 46 is respectively sleeved and connected to the portion 43 of the intake valve 41 and the exhaust valve 42 where the rod portion 43 is not penetrated, and is opposed to the second seat wall 342; when the first follower 31 When the second follower 32 is respectively displaced to the first position P1, the first seat wall 341 can be pressed against the first fixed ring sleeve 45 opposite to each other, and the opposite The steam valve 41 and the exhaust valve 42 close the opposite intake port 911 and exhaust port 921; when the first follower 31 and the second follower 32 are respectively displaced to the second position P2, The second seat wall 342 abuts the opposing second fixed ring sleeves 46 respectively, and the opposing intake valve 41 and exhaust valve 42 are linked to open the opposing intake ports 911 and exhaust口921.

In this embodiment, the first fixed ring sleeve 45 and the second fixed ring sleeve 46 are respectively inserted through the positioning pin 47 in the radial direction at the outgoing end 431 of the opposite rod portion 43 and not out The part 432 allows each other to be accurately and firmly connected to each other through assembly.

In this embodiment, the valve actuation mechanism 1 further includes at least two elastic support members 70, as shown in FIGS. 7 to 10, which are respectively disposed on the first fixed rings of the intake valve 41 and the exhaust valve 42 The sleeve 45, and the first seat wall 341 of the first follower 31 and the second follower 32 opposite to each other, so that the first follower 31 and the second follower 32 are located at the first At the position P1, the elastic restoring force of the elastic support member 70 is used to force the valve portions 44 of the intake valve 41 and the exhaust valve 42 to elastically press against the intake valve seat 91 and The exhaust valve seat 92 closely closes the intake port 911 and the exhaust port 921 opposite to each other.

In this embodiment, a spring positioning portion 451 is formed on each of the first fixed ring sleeves 45; the elastic support member 70 is a compression spring, which can be used to position the sleeve on the spring positioning portion 451. It should be particularly noted that the spring positioning portion 451 is substantially cylindrical, in addition to allowing the elastic prop 70 to be sleeved and positioned, the first seat wall 341 can also be provided by the bottom end wall surface 452 When the first follower 31 or the second follower 32 moves toward the first position P1, they abut against each other.

In this embodiment, when the first follower 31 and the second follower 32 are located at the first position P1, there is a formed between the first fixed ring sleeve 45 and each of the opposing first seat walls 341 In the first gap S1, a second gap S2 is formed between the second fixed ring sleeve 46 and each opposing second seat wall 342, as shown in FIG. 9; the first follower 31 and the second follower When 32 is located at the second position P2, a third gap S3 is formed between the first fixed ring sleeve 45 and each of the opposing first seat walls 341. As shown in FIG. 10, the third gap S3 is the first gap The sum of a gap S1 and a second gap S2, and the second fixed ring sleeve 46 and the opposing second seat walls 342 abut each other.

The purpose of setting the first gap S1 is to ensure that after the first follower 31 and the second follower 32 move from the second position P2 to the first position P1, the The elastic restoring force of the elastic jack 70 acts on the opposing first seat wall 341, so that the valve portion 44 of the opposing inlet valve 41 or exhaust valve 42 can be slightly upwardly displaced by elastic displacement, such as upward elasticity The displacement is 0.5 mm, and the elastic fit is tightly pressed against the opposite intake valve seat 91 or exhaust valve seat 92. In this way, the intake port 911 and the exhaust port 921 are tightly closed.

In other words, when the first follower 31 or the second follower 32 moves to the first position P1, the first seat wall 341 still bears against the first fixed ring sleeve 45 Without the design of the first gap S1, the valve portion 44 of the intake valve 41 or the exhaust valve 42 and the opposing intake valve seat 91 or exhaust valve seat 92 may cause a rigid collision with each other Damage, and at the same time, the impact force generated by the above collision may also be indirectly transmitted to the rotating assembly 33 via the first follower 31 or the second follower 32, thereby causing the rotating member 331, the mandrel 332 and other components Damage, therefore, the design of the first gap S1 can cleverly avoid the above-mentioned collision, and can also allow the elastic prop 70 to automatically play the role of the elastic prop during the final stroke of the follower The valve portion 44 can elastically fit against the intake valve seat 91 or the exhaust valve seat 92, and with the appropriate elastic force, the valve portion 44 is sufficiently resistant to combustion The vacuum of the chamber does not cause uncontrolled opening.

The purpose of setting the second gap S2 is to ensure that the valve portion 44 of the intake valve 41 or the exhaust valve 42 is used for a period of time due to its use in the valve portion 44 or the intake valve seat 91 and the exhaust valve seat 92 After abrasion, it can still be kept in a sealed state with the air inlet 911 and the air outlet 921.

Furthermore, if there is no design of the above-mentioned second gap S2, when the valve portion 44 of the intake valve 41 or the exhaust valve 42 or the intake valve seat 91 and the exhaust valve seat 92 are worn, due to The second fixed ring sleeve 46 has abutted against the opposite second seat wall 342, and does not allow the valve portion 44 of the intake valve 41 or the exhaust valve 42 to move upward and lift slightly. Therefore, the valve There will be a gap between the portion 44 and the opposite intake valve seat 91 or exhaust valve seat 92, and a complete sealing effect cannot be achieved.

Therefore, the design of the second gap S2 can effectively solve the above problem of inability to seal due to wear, so that the valve portion 44 can still communicate with the opposite air inlet 911 or exhaust within a certain wear range. The air port 921 is kept in a sealed state, for example, when the second gap S2 is set to 1 mm, and the amount of wear between the valve portion 44 and the opposite air intake port 911 or exhaust port 921 reaches 0.3 mm, while , When the first follower 31 or the second follower 32 moves to the first position P1, the valve portion 44 of the intake valve 41 or the exhaust valve 42 may also be allowed due to the elastic jack The elastic restoring force of 70 will move slightly upward to raise 0.3mm, so as to ensure that the valve portion 44 and the opposite air inlet 911 or air outlet 921 are kept in a sealed state.

It can be easily understood that at this time, the second gap S2 will decrease from 1 mm to 0.3 mm to 0.7 mm, and the first gap S1 will increase from 0.5 mm to 0.3 mm to 0.8 mm. From the above, if When the second gap S2 is set to 1 mm, the maximum wear amount allowed in this embodiment is 1 mm, that is, in principle, the normal wear state can be maintained within this maximum wear amount.

In this embodiment, the valve actuation mechanism 1 further includes at least two second elastic buffer members 80, as shown in FIGS. 7 to 10, respectively provided on the second fixing of the inlet valve 41 and the exhaust valve 42 The ring sleeve 46 and the intake valve seat 91 and the exhaust valve seat 92 facing each other can be displaced to the second position P2 between the first follower 31 and the second follower 32, respectively At this time, it is elastically compressed by the opposing second fixed ring sleeve 46 to provide the elastic cushioning effect required during the opening of the intake valve 41 and the exhaust valve 42. Furthermore, the bottom end of the second elastic buffer member 90 of this embodiment is pressed against the top wall surface 913 of the intake valve seat 91 and the top wall surface 923 of the exhaust valve seat 92, and the Between the top wall surfaces 913 and 923 and the opposite intake passage 912 and exhaust passage 922 are respectively provided with rod penetration holes 914 and 924, which can be used to penetrate the rod portions 43 of the opposite inlet valve 41 and exhaust valve 42 respectively Ever. In this embodiment, the top wall surface 913 and the top wall surface 923 are respectively formed at different positions on the same wall surface.

In this embodiment, the second elastic buffer member 80 is a compression spring, and is respectively positioned on the rod portions 43 of the intake valve 41 and the exhaust valve 42 opposite to each other.

In this embodiment, when the first follower 31 and the second follower 32 are located at the first position P1, the second fixed ring sleeve 46 is opposite to the opposite second elastic buffer member 80 It is separated by a distance d2, as shown in FIG. 9, so that the second elastic buffer member 80 only moves toward the second position P2 when the first follower 31 and the second follower 32 move The elastic cushioning effect occurs during the segment stroke, which means that the second elastic cushioning member 80 will not be affected by most of the strokes before the last stroke of the first follower 31 and the second follower 32 The displacement sliding of the first follower 31 and the second follower 32 generates any resistance, therefore, it can be ensured from the drive shaft 10's power will not suffer too much loss.

Furthermore, by the design of the distance d2, the stroke of the first follower 31 and the second follower 32 in the direction of the second position P2, that is, the intake valve 41 and the exhaust valve 42 About half of the strokes are empty strokes and the other half are elastic cushion strokes. The use of the empty strokes can reduce power loss. Using this elastic cushion stroke, in addition to exerting an elastic cushioning effect, to reduce or eliminate inertia The acting force can also be converted into an auxiliary force for the return stroke, that is, to provide the auxiliary force when the first follower 31 and the second follower 32 move in the direction of the first position P1, so as to reduce the rotating component 33 The resistance received when the transmission pulls the intake valve 41 and the exhaust valve 42 makes the transmission more labor-saving, thereby reducing wear and damage. Similarly, the first elastic buffer 60 can also achieve the same effect as the second elastic buffer 80.

Regarding the above-mentioned third gap s3, when the first follower 31 and the second follower 32 are displaced to the second position P2, their second seat walls 342 are respectively pressed against the opposite second fixings At the same time, each second fixed ring sleeve 46 abuts against and compresses the opposing second elastic buffer members 80. Therefore, naturally the first seat wall 341 and the first fixed ring sleeve 45 form the first Three gaps S3, in other words, the third gap S3 is the sum of the first gap S1 and the second gap S2. For example, when the first gap S1 is 0.5 mm and the second gap is 1 mm, then The third gap S3 is 1.5 mm.

It should be particularly noted that this embodiment only discloses the cylinder head 9 and the valve actuation mechanism 1 mounted on the cylinder head 9, but does not disclose other components, such as the spark plug and the fuel injector that are commonly installed on the cylinder head 9, The components such as the cylinder, the piston installed inside the cylinder, and the crankshaft connected to the piston are not disclosed, because these components are not the structural features to be improved by the present invention and are generally the same as the traditional structure and function, so they will not be repeated here. The structure of the cylinder head 9 of this embodiment also only shows that it is to be improved The general structure is not an actual complete or precise structure.

Secondly, the valve actuation mechanism 1 of the present embodiment uses a four-stroke, two-in, two-out internal combustion engine as a schematic structure, so it has two inlet valves 41 and two exhaust valves 42. Similarly, the cylinder head 9 also has two intake valve seats 91 and two exhaust valve seats 92. We know that the operation of the four-stroke internal combustion engine is divided into four strokes of intake, compression, power and exhaust. Therefore, the two intake valves 41 of this embodiment will synchronously open the intake during the intake stroke The air port 911 allows air or gas mixed with oil to enter the combustion chamber of the cylinder through the air intake passage 912 and the air intake port 911, and closes the air intake port 911 at the end of the intake stroke; the other two The exhaust valve 42 synchronously opens the exhaust port 921 during the exhaust stroke, so that the exhaust gas in the combustion chamber can be discharged from the exhaust port 921 through the exhaust passage 922, it is easy to imagine that , The opening degree of the intake valve 41 and the exhaust valve 42 when they are opened, and the timing of the switch, are the pre-designed contour curves of the cam grooves 23 of the first cam 21 and the second cam 22 of the cam assembly 20 , The first follower 31 and the second follower 32 of the driven assembly 30 are interlocked to control each other, but the openings of the inlet valve 41 and the exhaust valve 42, that is, their lift sizes, are not what we want to discuss The technical focus, the timing of its switching, which is the valve timing, is not the technical focus we want to discuss.

As shown in FIGS. 11 to 13, the present invention further provides a second embodiment of the valve actuation mechanism of the engine. The valve actuation mechanism 1a is substantially the same as the first embodiment, and the only difference is that: Although the intake valve 41 and the exhaust valve 42 of this embodiment are also connected to each of the opposed first follower 31 and the second follower 32 via the rod portion 43, the connection structure between them is compared to the above One embodiment is slightly different, that is, the rod portion 43 of this embodiment does not pass through the first follower 31 and the second follower 32, as shown in FIGS. 14 and 15, there is no first implementation The first fixed ring sleeve 45 and the second fixed ring sleeve 46 are taken by a spring assembly 100 and a push tube assembly 200 generation.

Furthermore, the valve actuating mechanism 1a of this embodiment further includes at least one spring assembly 100; the spring assembly 100 further includes a first extension spring 101 and a second extension spring 102, one end 103 of which is respectively Connected to the opposing first follower 31 and the second follower 32, and the other end 104 is respectively connected to the rod portion 43 of the opposing inlet valve 41 and the exhaust valve 42 to make the first follower When the 31 and the second follower 32 are respectively displaced to the first position P1, the intake valve 41 and the exhaust that are opposite to each other can be pulled through the first tension spring 101 and the second tension spring 102 respectively. The steam valve 42 further closes the intake port 911 and the exhaust port 921 opposite to each other. In this embodiment, two spring assemblies 100 are provided, that is, there are two first extension springs 101, which are connected to one first follower 31 and two second springs. The extension spring 102 is connected to one of the second followers 32 together.

In other words, the first follower 31 and the second follower 32 mainly use the spring assembly 100 as a connecting member to pull the intake valve 41 and the exhaust valve 42 connected to each other. The advantage is that the first follower 31 and the second follower 32 can be displaced to the first position by the elastic tension of the first tension spring 101 and the second tension spring 102 At P1, on the one hand, it can be ensured that the valve portion 44 of the inlet valve 41 and the exhaust valve 42 can elastically seal against the inlet port 911 and the exhaust valve seat 92 of each opposite intake valve seat 91 The exhaust port 921 achieves a good effect of closing the intake port 911 and the exhaust port 921, on the other hand, the valve portion 44 of the intake valve 41 and the exhaust valve 42 and the opposing intake port 911 can be avoided When it collides with the exhaust port 921, a rigid collision occurs, thereby preventing collision damage.

The valve actuation mechanism 1a of this embodiment further includes at least one push tube assembly 200; the push tube assembly 200 further includes a first push tube 201 and a second push tube 202, respectively The sleeve is positioned outside the first extension spring 101 and the second extension spring 102, and one end 203 respectively abuts the opposing first follower 31 and second follower 32, and the other end 204 respectively When the rod portions 43 of the opposing intake valve 41 and exhaust valve 42 are pressed against each other, when the first follower 31 and the second follower 32 are respectively displaced to the second position P2, they can respectively penetrate The first push pipe 201 and the second push pipe 202 are pushed to move the intake valve 41 and the exhaust valve 42 relative to each other, thereby opening the intake port 911 and the exhaust port 921. In this embodiment, a total of two push tube assemblies 200 are provided, that is, two first push tubes 201 are provided to jointly abut the first follower 31 and the two second The pushing tube 202 is used to jointly resist one of the second followers 32.

Compared with the steam valve assembly 40 of the first embodiment, the steam valve assembly 400 of this embodiment further includes at least two abutment nuts 401 screwed to the rod portions 43 of the intake valve 41 and the exhaust valve 42 respectively , The other ends 204 of the first push tube 201 and the second push tube 202 can be respectively pressed against each other, so as to move the corresponding intake valve 41 and exhaust valve 42 by pushing. In this embodiment, a total of four abutting nuts 401 are provided, which are respectively screwed to the rod portions 43 of the two intake valves 41 and the two exhaust valves 42.

The steam valve assembly 400 of this embodiment further includes at least two pressing nuts 402 screwed to the rod portions 43 of the intake valve 41 and the exhaust valve 42 respectively, the main purpose of which is to press the opposing head nuts 401, to prevent the abutment nut 401 from loosening during actuation. In this embodiment, a total of four pressing nuts 402 are provided, which are respectively screwed on the rod portions 43 of the two intake valves 41 and the two exhaust valves 42.

It can be seen from the above that the first follower 31 and the second follower 32 mainly push the inlet valve 41 and the exhaust valve 42 connected to each other through the push pipe assembly 200 as a connecting member. The advantage lies in that: by the first push tube 201 and the second push tube 202 rigidly contacting and pushing the opposing abutment nuts 401 on the rod portions 43, the pushing action can be ensured more accurately and quickly, without produce Any delay in time, especially when the engine is running at high speed, can ensure that the intake valve 41 and the exhaust valve 42 can accurately and quickly generate opening actions to complete a good intake and exhaust stroke.

This embodiment is also provided with the second elastic buffer member 80 of the first embodiment, the difference is that: this embodiment does not have the second fixed ring sleeve 46 of the first embodiment, therefore, two buckles 430 are separately provided The buckle is positioned on the rod portion 43 of the intake valve 41 and the exhaust valve 42 so that the second elastic buffer member 80, which can be a compression spring, can be inserted into each of the opposing intake valve 41 or exhaust valve 42 On the rod portion 43, and located between the retaining ring 430 and the top wall surface 913 of the intake valve seat 91 or the top wall surface 923 of the exhaust valve seat 92 opposite each other, so that when the first follower 31 When moving with the second follower 32 in the direction of the second position P2, the second elastic buffer members 80 can be elastically compressed by the opposing buckles 430, and provide the intake valve 41 and the exhaust The elastic damping required by the steam valve 42 during the opening process.

Similar to the first embodiment, when the first follower 31 and the second follower 32 of this embodiment are located at the first position P1, the retaining ring 430 and the second elastic buffer members 80 opposite to each other The opposite ends are separated by a distance d2, as shown in FIG. 14, so that the second elastic buffer 80 moves only in the direction of the second position P2 in the first follower 31 and the second follower 32 The elastic cushioning effect is generated in the last stage of the stroke, that is, the second elastic cushioning member 80 will not react to most of the strokes before the last stage of the first follower 31 and the second follower 32 The displacement sliding of the first follower 31 and the second follower 32 generates any resistance, and therefore, it can be ensured that the power from the drive shaft 10 is not too much consumed.

In this embodiment, when the first follower 31 and the second follower 32 are located at the first position P1, they are separated from the opposite ends of the opposite first push tube 201 and second push tube 202 by Four gaps S4, as shown in FIG. 14, but when located at the second position P2, they are pressed against the opposing The first push tube 201 and the second push tube 202 have opposite ends. Therefore, there is no fourth gap S4 between them, which means that the first follower 31 and the second follower 32 are located in the first In the position P1, the first extension spring 101 and the second extension spring 102 have a larger extension, which can generate a larger elastic tension to ensure the inlet valve 41 and the exhaust valve 42 The valve portion 44 can more closely abut against each of the opposing intake port 911 and exhaust port 921, so as to maintain a good sealing effect between each other. When the first follower 31 and the second follower 32 are located at the second position P2, since the elastic tension of the first tension spring 101 and the second tension spring 102 is not required, it can be allowed Less elongation.

It is easily conceivable that the size of the fourth gap S4 can be controlled by proper rotation of the counter nut 401 and the pressing nut 402, for example, the size of the fourth gap S4 can be increased by rotation , So that the elongation of the first extension spring 101 and the second extension spring 102 when the first follower 31 and the second follower 32 are at the second position P2 becomes smaller, but relatively Therefore, the opening amount or opening degree of the valve portion 44 of the intake valve 41 and the exhaust valve 42 relative to each intake port 911 and exhaust port 921 will also decrease accordingly.

In this embodiment, in order to ensure that the first extension spring 101 and the second extension spring 102 are connected to the first follower 31 and the second follower 32, the first follower 31 At least one lug 35 is protruded from each of the second followers 32, as shown in FIGS. 13 to 15, and a perforation 351 is provided on each lug 35, so that the first extension spring 101 and the second After the opposite ends of the tension spring 102 pass through the relative through holes 351, they can be connected to each other by a connecting rod 36 extending through each other, so that the first tension spring 101 and the second tension spring 102 can be connected It is smoothly connected to the opposing first follower 31 and second follower 32. In addition, the other ends of the first tension spring 101 and the second tension spring 102 can be positioned on the opposite intake valve 41 and exhaust valve by hooks respectively The rod 43 of 42 is connected to each other.

From the above description, it can be seen that the valve actuation mechanism 1, 1a of the engine of the present invention can be summarized as follows:

First, the present invention uses the structure of the conventional crankshaft to drive the camshaft through a timing belt or chain as the main driving structure, the difference is that the cam on the traditional camshaft is integrally formed, and the present invention is assembled from the drive shaft 10 to the first cam 21 It is composed of a second cam 22, and the first cam 21 and the second cam 22 of the present invention are slot-shaped cams, which can drive the intake valve 41 and the exhaust valve 42 to open However, the traditional cam can only provide one-way downward pressing force. Therefore, the present invention can properly retain the characteristics of the traditional driving structure without adding new or different power sources and driving structures, which can reduce the structure and reduce The cost of improvement, as well as the possibility of retrofitting or implementing materialization.

Second, the present invention retains the traditional power source and drive structure, which can ensure the reliability and stability of the power source, especially compared to the power source such as electric motor or solenoid valve, mechanical drive has relatively better reliability and stability degree.

Thirdly, the cam assembly 20 of the first embodiment of the present invention can directly open and close the valve assembly 40 through the cam slot 23 through the rotating assembly 33 and the driven assembly 30 to directly and rigidly actuate the valve assembly 40, thus avoiding the generation of traditional valve assemblies When it is opened, it is affected by the large elastic resistance of the spring, and when it is closed, it is limited by the limited elastic restoring force of the spring, resulting in a time lag phenomenon. Therefore, the traditional spring valve mechanism is likely to produce a piston at a high speed. The shortcomings of hitting a valve that has not been closed, and because the valve has not yet returned to the valve seat, resulting in a reduction in engine compression ratio and power loss, and even damage to the valve, can be effectively solved in the present invention. The second embodiment of the present invention is also the same, the difference is that the valve passes through the spring assembly 100 when the valve is closed, and passes through when the valve is opened The tube assembly 200 is pushed, but the achievable effect is about the same.

Fourthly, although the present invention is provided with springs, such as the first elastic buffer member 60, the second elastic buffer member 80 and the elastic support member 70 of the first embodiment, the first elastic buffer member 60 and the second elastic buffer member 80 is only used to provide cushioning in the final stroke of the valve, so the opening action of the valve does not cause excessive resistance or cause any hysteresis, that is, the valve is mostly maintained during the opening process. Free travel without resistance. In addition, the elastic jack 70 does not produce any damping effect during the closing stroke of the valve, but only uses its elastic restoring force at the moment of closing to keep the valve a certain urging force to ensure sufficient sealing effect against the roof Therefore, it will not cause resistance or cause any lag to the closing stroke of the valve. Therefore, the valve actuating mechanism 1, 1a of the present invention can ensure that the valve is opened and closed quickly and accurately, so it can fully meet the engine The demand for valve actuation at high speeds. The second embodiment is substantially the same. The difference is that the spring assembly 100 is used to simultaneously replace the elastic support member 70 of the first embodiment.

Fifth, since the steam valve of the present invention is generally not affected by spring resistance during the opening and closing process, that is, it is mostly in the state of idle travel, therefore, its timing belt or chain rotation resistance is small, and it does not consume too much. Engine output power can effectively improve engine power output efficiency.

Sixth, the first embodiment of the present invention utilizes the design of the first gap S1 and the second gap S2, which can reserve an appropriate dimensional margin to eliminate manufacturing tolerances, and can also cause wear between subsequent valves and valve seats. It can still maintain normal operation without affecting the efficiency of the valve switch.

Seventh, between the guide slider 51 and each follower in the first embodiment of the present invention, and the positioning seat 94 and each follower are provided with a limit structure for moving up and down, for example, on the guide slider 51 The limiting protrusion 511 and the limiting wall 942 on the positioning seat 94 can be designed to effectively avoid the followers, etc. The inertial force generated when the linking member slides upward and downward causes damage to the rotating member 331 or the mandrel 332, etc. Therefore, the service life of the rotating member 331, the mandrel 332 and other related members can be ensured.

In summary, the present invention has excellent creative practicality among similar products. At the same time, it has searched relevant technical information or patent documents at home and abroad, and it has not been found that the same structure is disclosed first. Therefore, the present invention has the invention For patent requirements, you must apply according to law. However, the above is only a part of the feasible embodiments of the present invention, and any equivalent structural changes that apply to the description of the present invention and the scope of patent application should be included in the patent scope of the present invention.

10: Drive shaft

21: First cam

23: cam slot

31: First follower

33: Rotating components

331: Rotating parts

332: Mandrel

34: Shaft seat

341: The first wall

342: Second wall

343: Shaft hole

41: Intake valve

43: Rod

44: Valve

45: First fixed ring sleeve

46: Second fixed ring sleeve

50: Guide slide assembly

51: Guide slider

511: limit protrusion

70: Elastic top support

80: second elastic buffer

9: cylinder head

9a: Base part

9b: Wall part

91: Intake valve seat

911: Air intake

912: Intake passage

913: top wall surface

94: positioning seat

942: Limit wall

P1: first position

d1: distance

Claims (25)

An engine valve actuation mechanism can be installed on a cylinder head of the engine, and the cylinder head has at least one intake valve seat and at least one exhaust valve seat, each of which is formed There is an intake port, and an intake channel is provided to communicate with the intake port, each exhaust valve seat is formed with an exhaust port, and an exhaust channel is provided to communicate with the exhaust port; the valve is actuated The mechanism includes: a drive shaft pivotably connected to the cylinder head; a cam assembly, including a first cam and a second cam, which can be fixed to the drive shaft; a driven The assembly, including a first follower and a second follower, can be driven by the first cam and the second cam, respectively, and is restricted to linearly reciprocate between a first position and a second position One valve assembly, including at least one intake valve and at least one exhaust valve, can be installed on the intake valve seat and exhaust valve seat, and each has a rod portion, and a self A valve portion extending at one end of the rod portion, the rod portion being respectively connected to the opposing first follower and the second follower, and the valve portion can respectively open or close the opposing intake and exhaust ports; When the first follower and the second follower are respectively displaced to the first position, the respective intake and exhaust valves can be respectively linked to close the respective intake and exhaust ports; When the first follower and the second follower are respectively displaced to the second position, the opposite intake and exhaust valves can be respectively linked to open the opposite intake and exhaust ports; wherein, Both the first cam and the second cam are slot-shaped cams, and a cam slot is formed on each of them; the driven component further includes two rotating components, which are respectively fixed to the first driven component and the second driven component On the component, the rotating components each include a rotating component, which is rotatable It is accommodated in the cam grooves of the opposing first cam and the second cam, and can link the opposing first follower and the second follower with the rotation of the first cam and the second cam Pieces. The valve actuation mechanism for an engine according to claim 1, wherein the rotating member is a bearing. The valve actuation mechanism of the engine according to claim 1 further includes a second guide slide assembly; the guide slide assemblies each include a second guide slider, and are arranged on the cylinder head at relatively intervals, which can be formed between each other A guide groove, so that the first follower and the second follower can be restricted to linearly reciprocate in the guide groove. The valve actuation mechanism of the engine according to claim 3, wherein a limit structure is provided between the guide slider and the opposing first follower or second follower to make the first follower Or when the second follower is displaced to the first position, it can be limited by the limit structure, the limit structure includes a limit protrusion formed on the guide slider, and the first follower The relative abutment position on the component or the second follower. The valve actuation mechanism of the engine according to claim 1 further includes two first elastic buffer members, which are fixed to the cylinder head and are opposed to the first follower member and the second follower member, And when the first follower and the second follower move toward the second position, they are elastically compressed by the opposing first follower and second follower to provide the first The elastic buffering function required by the follower and the second follower during the actuation process. The engine valve actuation mechanism according to claim 5, wherein the cylinder head has two positioning seats, each of the positioning seats has a spring accommodating groove; the first elastic buffer member is a compression spring, which One end is respectively accommodated in the spring accommodating grooves positioned in the relative positioning seats, and the other end is provided for the opposing first follower and the second follower to bear against each other. The valve actuation mechanism of the engine according to claim 6, wherein a positioning structure is provided between the positioning seat and the opposing first follower or second follower to make the first follower or When the second follower is displaced to the second position, it is limited by the limit structure, the limit structure includes a limit wall formed on the positioning seat, and the first follower or the first The relative position of the two followers is against the top. The valve actuation mechanism for an engine according to claim 5, wherein when the first follower and the second follower are in the first position, they are separated from the opposite end of the opposing first elastic buffer There is a distance so that the first elastic cushioning member only generates an elastic cushioning effect in the last stage of the movement of the first driven member and the second driven member toward the second position. The valve actuation mechanism for an engine according to claim 1, wherein the first follower and the second follower are each provided with a shaft seat, and the shaft seats each have a first seat wall opposite to The first cam and the second cam, and each has a second seat wall relative to the intake valve seat and the exhaust valve seat, and the first seat wall and the second seat wall of the shaft seat Each shaft is provided with a shaft hole through which the free ends of the rod portions of the opposite inlet and exhaust valves can pass through and protrude; the steam valve assembly further includes at least two first fixing ring sleeves and at least two second fixings A ring sleeve, the first fixed ring sleeves are respectively sleeved and connected to the rod outlets of the intake valve and the exhaust valve, and are opposite to the first seat wall; the second fixed ring sleeves are respectively The sleeve is connected to the portion of the intake valve and the exhaust valve that does not penetrate the rod, but is opposed to the second seat wall; when the first follower and the second follower are respectively displaced to the first In one position, the first seat wall can be pressed against the opposing first fixed ring sleeves, and the opposing intake and exhaust valves can be linked to close the opposing intake and exhaust ports. When the first follower and the second follower are respectively displaced to the second position, the second seat ring can be pressed against the opposite second fixed ring sleeves respectively, and the relative steam inlet can be linked Door and exhaust valve open each phase The right inlet and outlet. The engine valve actuation mechanism according to claim 9 further includes at least two elastic jacks, which are respectively disposed on the first fixed ring sleeves of the intake valve and the exhaust valve, and the opposing first slaves Between the first seat wall of the moving member and the second driven member, when the first driven member and the second driven member are in the first position, the elastic restoring force of the elastic supporting member , Forcing the valve portions of the intake valve and the exhaust valve to elastically press against the opposing intake valve seat and exhaust valve seat, thereby tightly closing the opposing intake and exhaust ports. The engine valve actuation mechanism according to claim 10, wherein each of the first fixed ring sleeves is formed with a spring positioning portion, and the spring positioning portion further has a bottom end wall surface, The seat walls abut against each other as the first follower or second follower moves toward the first position; the elastic support member is a compression spring, which can be used to position the sleeve on the spring unit. The valve actuation mechanism for an engine according to claim 10, wherein when the first follower and the second follower are in the first position, the first fixed ring sleeve and each of the opposing first A first gap is formed between the seat walls, a second gap is formed between the second fixed ring sleeve and each of the opposing second seat walls; the first follower and the second follower are located at the second position At this time, a third gap is formed between the first fixing ring sleeve and each opposing first seat wall, the third gap is the sum of the first gap and the second gap, and the second fixing ring sleeve The second seat walls opposing each other abut each other. The valve actuation mechanism of the engine according to claim 9, further comprising at least two second elastic buffers, which are respectively disposed on the second fixed ring sleeves of the intake and exhaust valves, and the opposite intake air Between the valve seat and the exhaust valve seat, the first follower and the second follower can be respectively displaced When it reaches the second position, it is elastically compressed by the opposing second fixed ring sleeves to provide the elastic buffering function required for the intake valve and the exhaust valve during the opening process. The valve actuation mechanism for an engine according to claim 13, wherein when the first follower and the second follower are in the first position, the second fixed ring sleeve and the second The elastic buffer members are separated by a distance from each other, so that the second elastic buffer member only generates elastic cushion during the final stroke of the first driven member and the second driven member moving toward the second position effect. The valve actuation mechanism of an engine according to claim 13, wherein the second elastic buffer member is a compression spring, and is respectively positioned on the rod portions of the opposite intake and exhaust valves. The engine valve actuation mechanism of claim 1 further includes at least one spring assembly; the spring assembly further includes a first extension spring and a second extension spring, one ends of which are respectively connected to the respective A follower and a second follower, the other ends are respectively connected to the rod portions of the opposite inlet and exhaust valves, so that the first follower and the second follower are respectively displaced to the first When in position, the corresponding intake and exhaust valves can be linked through the first tension spring and the second tension spring, respectively, so as to close the opposite intake and exhaust ports. The valve actuation mechanism of the engine according to claim 16 further includes at least one push tube assembly; the push tube assembly further includes a first push tube and a second push tube, which are respectively sleeved and positioned on the first The outside of the extension spring and the second extension spring, and one end is respectively pressed against the opposing first follower and the second follower, and the other end is respectively pressed against the rods of the opposite inlet and exhaust valves When the first follower and the second follower are respectively displaced to the second position, they can move through the first push pipe and the second push pipe to move the opposite inlet valve and exhaust The steam valve, in turn, opens the opposite intake and exhaust ports. The valve actuation mechanism of the engine according to claim 17, wherein the valve assembly further includes at least two abutment nuts, which are screwed to the rod portions of the intake and exhaust valves, respectively The other ends of the first push pipe and the second push pipe are relatively opposed to each other, so as to move and move the relative inlet and exhaust valves. The valve actuation mechanism of the engine according to claim 18, wherein the valve assembly further includes at least two compression nuts, which are screwed to the stem portions of the intake and exhaust valves, respectively Press tightly against the opposing nuts. The valve actuation mechanism for an engine according to claim 16, wherein the valve assembly further includes at least two retaining rings that can be snapped and positioned on the stems of the intake and exhaust valves, respectively. The valve actuation mechanism of the engine according to claim 20, further comprising at least two second elastic buffers, which are respectively provided on the retaining rings of the intake valve and the exhaust valve, and the intake valve seats opposite to each other And the exhaust valve seat, when the first follower and the second follower are respectively displaced to the second position, they are respectively compressed by the elastic buckles of the opposing buckles to provide the intake steam The elastic buffering effect required by the door and exhaust valve during the opening process. The valve actuation mechanism for an engine according to claim 21, wherein when the first follower and the second follower are in the first position, the retaining ring and the second elastic buffers opposite to each other The opposite ends are separated by a distance, so that the second elastic cushioning member only generates an elastic cushioning effect in the last stage of the movement of the first driven member and the second driven member toward the second position. The valve actuation mechanism for an engine according to claim 21, wherein the second elastic buffer member is a compression spring, and is respectively positioned on the rod portions of the opposite intake and exhaust valves. The valve actuation mechanism for an engine according to claim 17, wherein when the first follower and the second follower are in the first position, the first push tube and the second push Guan Xiang There is a fourth gap at the opposite end. The valve actuation mechanism for an engine according to claim 16, wherein the first follower and the second follower respectively have at least one lug, and a perforation is provided on each lug; the first After the ends of the extension spring and the second extension spring with respect to the lugs respectively pass through the corresponding perforations, they can be connected to each other by a connecting rod extending through each other; the first extension spring and the second The other ends of the tension springs can be hooked and positioned on the rod portions of the opposite inlet and exhaust valves respectively.

Images