TWI479076B - Engine variable valve lift mechanism - Google Patents

Description

Engine variable valve lift mechanism

The invention relates to a variable valve head mechanism of an engine, in particular to an engine variable valve head mechanism capable of obtaining an optimum power for an engine in a low speed running state and a high speed running state.

Referring to Figure 1, the first and second rocker arms 21, 22 are disposed above the valve valve 2, wherein the second rocker arm 22 is a multi-link member, with the first and second shaking The arms 21, 22 can respectively push the valve 2 to change the head of the valve 2, that is, when the first rocker 21 is pushing the valve 2, the valve 2 is a small opening; When the two rocker arms 22 push the valve 2, the valve 2 is the head of the maximum opening degree, thereby switching between the inlet and the exhaust valves of the different valve valves 2 in response to the high and low speeds of the engine 1.

The valve variable head mechanism of the engine 1 is configured to respectively push the valve 2 by the first and second rocker arms 21 and 22 above the valve 2, although it can be different when the engine 1 is operated at a high speed and a low speed. The inlet and exhaust valves of the valve 2 are switched. Since the first and second rocker arms 21, 22 are made of a heavier cast iron material, the moment of inertia is larger, and therefore the force of the valve spring 23 needs to be set stronger to overcome the moment of inertia. This also causes the engine power loss to be large; in addition, the second rocker arm 22 is a multi-link type structure, and the cylinder head 1a of the engine 1 is relatively necessary because of its complicated structure and a certain working space when it is required to operate. Larger size, in order to have enough space for the second rocker arm 22 to operate; the cylinder head 1a of the engine 1 is enlarged, which undoubtedly causes an increase in the cost of the engine 1, and the difficulty in setting the engineering design of the engine 1, as far as the locomotive is concerned Setting the space for Engine 1 is inherently limited. Therefore, how to improve the structure of the valve variable head mechanism of the relatively simple engine 1 is an urgent problem for the locomotive manufacturers.

The present invention mainly provides an engine variable valve lift mechanism having a cylinder head having an intake port and an intake valve, an exhaust port and an exhaust valve, and the intake port A camshaft seat is disposed between the exhaust rafts, and the camshaft seat is pivotally provided with a camshaft, wherein the camshaft is provided with a long intake cam, a short intake cam and an exhaust cam, when the camshaft rotates The intake valve rocker arm and the exhaust valve rocker arm can be pushed to make the intake valve and the exhaust valve act; the rocker arm of the intake valve and the rocker arm of the exhaust valve are made of light metal alloy, thereby effectively reducing the intake air. The moment of inertia of the valve rocker arm and the exhaust valve rocker arm can reduce the power consumption of the engine.

The above-mentioned intake valve rocker arm has a general opening degree rocker arm and a high opening degree rocker arm, and the general opening degree rocker arm is provided with a shaft hole, a through hole, a roller and a pressing portion, and the high opening degree rocker arm has a shaft hole, The through hole and the roller, the exhaust valve rocker arm has a shaft hole and a roller, and the shaft hole of the general opening degree rocker arm and the high opening degree rocker arm is provided with a rocker arm shaft, and the first one is connected with the oil control valve a driving oil passage and a second driving oil passage, wherein the rocker arm shaft is provided with a partition wall for separating the first driving oil passage and the second driving oil passage, and the roller of the general opening degree rocker arm is connected with the short intake air The cam rolling contact, and the pressing portion of the general opening rocker arm is in contact with the intake valve, and the roller of the high opening degree rocker arm is in rolling contact with the long intake cam, wherein the general opening degree of the rocker arm The inner wall surface of the through hole of the hole and the high opening degree rocker arm is wear-resistant material, and can be connected to form a hydraulic cylinder, and the first hydraulic piston has the first piston and the second with wear-resistant high toughness material. The piston can avoid the wear of the inner wall surface of the hydraulic cylinder of the intake rocker arm made of light metal and the first piston and the second piston, thereby effectively preventing oil pressure The amount of leakage to avoid problems due to insufficient hydraulic piston can not be pushed to a predetermined position occurs.

Ports communicating with the first oil passage and the second oil passage are respectively disposed near both ends of the hydraulic cylinder, and the first piston and the second piston are movable by the oil pressure output by the oil control valve. Therefore, when the engine is in a high-speed running state, the first piston and the second piston are moved to a joint position of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm, and the high opening degree rocker arm is generally The opening rocker arm is in a linkage mode; when the engine is in a low speed running state, the first piston and the second piston are respectively separated from each other in the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm. The high-opening rocker arm and the general opening rocker arm are in a mode of operation, thereby enabling the engine to obtain the optimum power in the low-speed running state and the high-speed running state.

The high-opening rocker arm and the light metal of the general opening rocker arm and the exhaust valve rocker arm are selected from at least one metal containing aluminum or magnesium as a main component; the through hole of the high opening degree rocker arm and the general opening degree rocker arm The wear-resistant material of the inner wall of the hole is selected as high-carbon steel; the high-toughness material of the first piston and the second piston is made of tool steel, so that the wear can be effectively prevented, and the oil pressure is largely leaked.

The high opening degree rocker arm and the general opening degree rocker arm, and the inner wall surface of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm are formed by bushings of different processes; The bushing of the arm through hole and the through hole of the general opening rocker arm are formed by at least one of embedding, pressing and punching; the shaft hole of the high opening rocker arm and the hole of the shaft hole of the general opening rocker arm The wall is made of wear-resistant material.

The camshaft is a single camshaft coaxially provided with a long intake cam, a short intake cam and an exhaust cam, which can make the components in the cylinder head more compact, avoiding the huge cylinder head, and benefiting the cylinder head on the whole vehicle. Space configuration.

The cylinder head further comprises a foot support mechanism for abutting the high opening degree rocker arm and the general opening degree rocker arm, the foot support mechanism comprising a foot support tube, a foot support spring and a spring for accommodating the foot support tube and the foot support spring The foot opening hole; the high opening degree rocker arm and the general opening degree rocker arm are further provided with a foot support portion, and the foot support portion is in contact with the foot support tube of the foot support mechanism to ensure the through hole of the high opening degree rocker arm And the through hole of the general opening rocker arm can be located at the set position.

The high opening degree rocker arm and the foot portion of the general opening degree rocker arm are located between the shaft hole and the pressing portion, so that the high opening degree rocker arm and the general opening degree rocker arm can be effectively located at a predetermined position.

The through hole of the high opening rocker arm and the through hole of the general opening rocker arm are located between the roller and the shaft hole and are located above the line connecting the center point of the roller and the shaft hole, thereby suppressing the overall length of the rocker arm It saves space for the rocker arm and avoids the problem of insufficient space in the cylinder head in a huge way.

The two ends of the hydraulic cylinder are respectively provided with a plug cover, and the plug cover protrudes from the inner side of the hydraulic cylinder, so that a certain pushing space is maintained between the hydraulic cylinder and the driving oil passage, so that the piston cannot be pushed. The problem has happened.

The through hole of the general opening rocker is provided with a return spring, and the return spring is in contact with the first piston, so that the oil pressure of the first driving oil passage does not need to be set too high, so that the piston can be moved, thereby saving The kinetic energy of the oil pump, and the first piston are provided with a first groove and a second groove, thereby making the piston lighter and more easily pushed by oil pressure or spring.

Regarding the structure of the present invention and the achievable effects, the following description is in conjunction with the following:

Referring to FIG. 2, the engine 3 of the present invention has a crankcase 31, a set of cylinder bodies 32 disposed on the crankcase 31, and a plurality of cylinder heads 33 disposed on the cylinder body 32; the crankcase 31, the interior A crankshaft (not shown) is provided, and an oil pump 311 is provided to deliver the oil to a main oil supply passage 312 which is passed through the cylinder body 32 through the crankcase 31. It is connected to the oil control valve 4 disposed on the cylinder head 33; the cylinder body 32 is disposed above the crankcase 31 and is configured to pass the timing chain 5, wherein the cylinder body 32 is in the intake port 331 of the cylinder head 33. A timing chain tensioner 51 is provided on the side.

The cylinder head 33 is provided with an intake port 331 and an intake valve 332 on the intake side, and an exhaust port 333 and an exhaust valve 334 on the exhaust side. Please refer to Figures 2, 3, 4 and 5 for reference. The cylinder head 33 is integrally formed between the intake port 331 and the exhaust port 333. A cam shaft seat 335 is provided. The cam shaft base 335 is provided with a cam shaft 336 that can be driven by the timing chain 5, and the cam shaft 336. The upper intake cam 3361 (high lift cam), the short intake cam 3362 (low lift cam) and the exhaust cam 3363 are respectively provided by the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363. The camshaft 336 can push the intake valve rocker arm 6 and the exhaust valve rocker arm 7 of the intake valve 332 and the exhaust valve 334 to open and close when rotating; the intake valve rocker arm 6 and the exhaust valve The valve rocker arm 7 is made of a light metal alloy, and the light metal alloy has a main component of aluminum or magnesium as a main component; the rocker arm thus formed has a light mass and a small moment of inertia, so the intake valve 332 and the exhaust valve The force of the valve spring 33a of 334 need not be set too high, that is, the moment of inertia can be overcome, so that the power consumption of the engine can be reduced. Therefore, the loss of kinetic energy is effectively avoided; in addition, the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363 are coaxially disposed on the single camshaft 336, so that the parts in the cylinder head 33 can be more compactly arranged and the cylinder can be avoided. The head 33 is enlarged to benefit the space configuration of the cylinder head 33 on the entire vehicle.

Referring to FIG. 3, FIG. 5 and FIG. 6, the exhaust valve rocker arm 7 has a shaft hole 712 through which the exhaust rocker arm shaft 74 is disposed. One end of the exhaust valve rocker arm 7 is a pressing portion 71. The pressing portion 71 is in contact with the exhaust valve 334, and the end of the pressing portion 71 has a gap adjusting member 711, and the other end is a roller 72 which is in rolling contact with the exhaust cam 3363, and the exhaust valve rocker arm 7 A sleeve 73 forming a shaft hole 712 is integrally formed on one side for the rocker shaft 74 to pass through, and the rocker arm shaft 74 is used to stably position the exhaust valve rocker arm 7 on the cam shaft seat 335. The roller 72 can be pushed by the exhaust cam 3363 of the cam shaft 336 to press the pressing portion 71 against the exhaust valve 334, thereby opening the exhaust valve that is normally closed to discharge the exhaust gas, and the pressing portion 71 and the exhaust valve The gap of 334 can be adjusted by the gap adjusting member 711, whereby the head of the exhaust valve 334 can be ensured.

Referring to FIG. 3, FIG. 5 and FIG. 7, the intake valve rocker arm 6 has a high opening rocker arm 61 and a general opening rocker arm 62. The high opening degree rocker arm 61 has a shaft hole 611 in front of the shaft hole. Before the 611, the foot support portion 612 is convexly disposed, and the through hole 613 is disposed behind the shaft hole 611, and the roller 614 is disposed behind the through hole 613; the general opening degree rocker arm 62 and the high opening degree rocker arm 61 is correspondingly provided with a foot support portion 622, a shaft hole 621, a through hole 623 and a roller 624. Further, the general opening degree rocker arm 62 extends a front end edge of the foot support portion 622 with a pressing portion 625. The pressing portion 625 The front end is provided with a gap adjusting member 6251; the roller 614 of the high opening degree rocker arm 61 is in rolling contact with the long intake cam 3361 of the cam shaft 336, and the roller 624 of the general opening degree rocker arm 62 is a cam shaft The short intake cam 3362 of the 336 is in rolling contact, and the pressing portion 625 of the general opening rocker 62 is in contact with the intake valve 332. The gap between the pressing portion 625 and the intake valve 332 can be obtained by the gap adjusting member 6251. Adjustment, thereby ensuring the lift of the intake valve 332, and passing through the rocker shaft 63 through the shaft holes 611, 621, thereby enabling the high opening rocker arm 61 and the general opening rocker arm 62 The high-opening rocker arm 61 and the general opening rocker arm 62 are swingably centered on the rocker arm shaft 63, and the rocker arm shaft 63 is positioned on the camshaft seat 335. As shown in FIG. 3, the high-opening rocker arm 61 and the foot support portions 612 and 622 of the general opening degree rocker arm 62 are located between the shaft holes 611 and 621 and the pressing portion 625. The through holes 613, 623 of the arm 61 and the general opening rocker arm 62 are located between the rollers 614, 624 and the shaft holes 611, 621, and are located at the center points of the roller holes 614, 621 and the shaft holes 611, 621, respectively. Above the line A, the overall length of the intake rocker arm 6 can be suppressed, space is saved, and the cylinder head 33 can be prevented from overcoming the problem of insufficient space in a huge manner; please refer to Figure 5, 7, 8, and 9 for details. The through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 communicate with each other to form a hydraulic cylinder 64, wherein the general opening degree rocker arm 62 has a through hole 623 and a high opening degree. The inner wall surface 613a of the through hole 613 of the rocker arm 61 is wear-resistant material The inner surface 613a of the wear-resistant material may be formed by electroplating or heat treatment or coating; the inner wall surface 613a of the wear-resistant material may also be made of bushings of different processes. The bushing can be combined with the through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 in at least one manner of embedding, pressing, and projecting, thereby avoiding the progress made of light metal. The wear of the inner wall of the hydraulic cylinder 64 of the air rocker arm 6 can effectively prevent a large amount of oil pressure from leaking. In addition, the high-toughness material of the wear resistance can be formed only on the piston surface 643a.644a; the two ends of the hydraulic cylinder 64 are respectively A plug cover 641a.641b is disposed, and the plug cover 641a.641b protrudes from the hydraulic cylinder 64 with a protrusion 6411a.6411b. The hydraulic cylinder 64 is provided with a first piston 643 and a hydraulic pump The second piston 644, the first piston 643 and the second piston 644 have a wear-resistant high toughness material, and the wear-resistant high toughness material can be selected from tool steel, thereby avoiding the inner wall of the hydraulic cylinder 64 with the intake rocker arm. The abrasion can effectively prevent a large amount of oil pressure leakage; the hydraulic cylinder 64 is driven by the first and second driving oil passages 6 5, 66 and communicate with the oil control valve 4, thereby obtaining a power oil source, and the first side of the first piston 643 is provided with a first groove 6431 and a second groove 6432, thereby reducing the weight of the first piston 643 The first groove 6431 can be accommodated in the boss 6411a of the plug cover 641a, that is, the first groove 6431 is the plug cover 641a. The protrusions 6411a are matched, and the protrusions 6411b of the cover 641b are opposite to one side of the second piston 644. The first piston 643 and the second piston 644 are formed at a distance from the two ends of the hydraulic cylinder 64, so that the first and second driving oil passages 65 and 66 can enter the power oil source in the hydraulic cylinder 64, and the smooth flow can be smoothly performed. Pushing the first piston 643 and the second piston 644 by the bosses 6411a.6411b of the plug cover 641a.641b, the first piston 643 and the second piston 644 can be positioned at a predetermined position when actuating The movement of the first piston 643 and the second piston 644 in the hydraulic cylinder 64 can be ensured. The cylinder head 33 below the foot support portions 612 and 622 is provided with a foot support mechanism 337. The foot support mechanism 337 includes a foot. The support tube 3371, the one foot support spring 3372 and the foot support hole 3373 are formed by the foot support mechanism 337 for contacting the foot support portions 612 and 622, thereby ensuring the through hole 613 of the high opening degree rocker arm 61 and the general opening degree. The through hole 623 of the rocker arm 62 can be located at a set position. When the foot support mechanism 337 is subjected to an excessive abutting force of the foot support portions 612 and 622, the foot support hole 3373 can release the pressure in time to ensure the oil pressure. The mobility of the first piston 643 and the second piston 644 within the cylinder 64.

When the present invention is implemented, as shown in FIG. 8 and FIG. 9, the rocker arm shaft 63 is provided with a partition wall 631 for separating the first driving oil passage 65 and the second driving oil passage 66. The partition wall 631 is disposed. It is integrally extended by the rocker shaft 63, so there is no need to additionally install other stop separating elements, which can effectively reduce the number of parts and eliminate the assembly work; please refer to the second, third, eighth and ninth, by the crankcase The oil pump 311 provided in 31 sends the oil to a main oil supply passage 31. 2, the main oil supply passage 312 is communicated from the crankcase 31 through the cylinder body 32 to the oil control valve 4 disposed in the cylinder head 33, wherein the oil control valve 4 then feeds the oil to the first drive of the cylinder head 33. After entering the oil passage 65 and the second driving oil passage 66, the hydraulic cylinder 64 is again inserted into the hydraulic cylinder 64. In addition, please refer to FIG. 8 and FIG. 9 to sense the vehicle by the control center ECU (not shown) of the engine 3. After the driving state, if only the engine is running at a low speed, the control center ECU of the engine 3 can cause the oil control valve 4 to enter the oil from the driving oil passage 65 into the hydraulic cylinder 64, as shown in FIG. The pressure acts to move the first piston 643 and the second piston 644 toward the high-opening rocker arm 61. After the oil enters the through hole 621 of the general opening rocker arm 62 from the driving oil passage 65, the convexity is blocked by the plug cover 641a. The guide 6411a and the first piston 643 are guided into the recess 6431 of the first piston 643, while the oil located at the high opening rocker 61 is discharged from the drive oil passage 66, thereby causing the second piston 644 to be at a high position. The separation position in the rocker arm 61 is opened and can be positioned by the protrusion 6411b of the plug cover 6411b on the side of the high opening rocker 61. Position, and the first piston 643 can be positioned in a separate position within the general opening rocker arm 62. At this time, the high opening degree rocker arm 61 and the general opening degree rocker arm 62 are in respective actuation modes due to the general opening degree rocker arm. The front end pressing portion 625 is in contact with the intake valve 332, and the roller 624 behind the general opening degree rocker arm 62 is in rolling contact with the short intake cam 3362 (ie, the low lift cam) of the cam shaft 336. When the engine 3 intake steam valve 332 is in a low lift state; When the driving state is changed to the high-speed running state, the control center ECU of the engine 3 can cause the oil control valve 4 to enter the oil from the driving oil passage 66 into the hydraulic cylinder 64. As shown in FIG. 9, the oil will flow from the driving oil passage 66. In the through hole 613 of the high opening degree rocker arm 6, while the oil in the through hole 623 of the general opening degree rocker arm 62 flows out, the first piston 643 and the second piston 644 are driven to the general opening by the action of the oil pressure of the oil. The rocker arm 62 is displaced in the direction, so that the first piston 643 is located in the general opening rocker arm 62, and can be restrained by the boss 6411a of the plug cover 641a of the general opening rocker arm 62, the first piston 643 and the second piston 643 The piston 644 is positioned at an appropriate position, so that the second piston 644 is positioned at a combined position between the high opening rocker arm 61 and the general opening rocker arm 62, at which time the high opening rocker arm 61 and the general opening degree are shaken. The arm 62 is in the interlocking mode, because the roller 614 behind the high opening rocker arm 61 is in rolling contact with the long intake cam 3361 (ie, the high lift cam) of the cam shaft 336, and the front end of the general opening rocker 62 is pressed. The portion 625 is in contact with the intake valve 332, so that the general opening degree rocker arm 62 is driven by the high opening degree rocker arm 61, that is, The degree of raising of the intake cam 3361 (ie, the high lift cam) causes the intake valve 332 to reach a predetermined high-speed engine running state, thereby achieving the purpose of the engine 3 variable valve head; and, in addition, the general opening degree The through hole 623 of the rocker arm 62 is disposed to return to the spring 642. The return spring 642 is in contact with the first piston 643, whereby the oil pressure of the first driving oil passage 65 does not need to be set too high to push the piston to move. Save the kinetic energy of the oil pump 311 and avoid using only the return spring alone 642 causes the piston 643, 644 to move to a predetermined position after the elastic force is attenuated; in practice, the shaft hole 611 of the high opening rocker arm 61 and the shaft hole 621 of the general opening rocker arm 62 and the exhaust rocker arm The hole wall of the 7-axis hole 712 is made of wear-resistant material, and the wear-resistant material can be made of high-carbon steel; the above-mentioned hole wall can be formed by electroplating or heat treatment or coating; the hole wall of the wear-resistant material can also be different The bushing of the process is formed; the bushing can be combined with the shaft holes 611, 621, and 712 in at least one manner of being embedded, pressed, and shot, thereby avoiding the intake rocker arm 6 and the exhaust shake made of light metal. The wear of the wall faces 611, 621, and 712 of the arm 7 and the rocker shafts 63 and 74 can effectively improve durability.

The utility model has the advantages that the camshaft 336 is provided with a long intake cam 3361, a short intake cam 3362 and an exhaust cam 3363, respectively, and the intake valve rocker arm 6 has a high opening rocker arm 61 and a general opening degree. The rocker arm 62 is connected to the through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 to form a hydraulic cylinder 64, and a hydraulic cylinder 64 is provided in the hydraulic cylinder 64. The hydraulic pressure pushes the first piston 643 and the second piston 644, so that the high opening rocker arm 61 and the general opening rocker arm 62 can be oscillated or interlocked to make the head of the engine 3 into the valve 332. The change can further simplify the engineering of the variable lift of the engine 3 valve 332. Since the intake valve rocker arm 6 and the exhaust valve rocker arm 7 are rocker arms made of light weight light metal alloy material, the moment of inertia is small, so the valve springs of the intake valve 332 and the exhaust valve 334 The 33a force does not need to be set too high, that is, it can overcome the moment of inertia, so it can reduce the power consumption of the engine and effectively avoid the loss of kinetic energy. Furthermore, the inner hole surface 623 of the general opening degree rocker arm 62 and the inner wall surface 613a of the through hole 613 of the high opening degree rocker arm 61 are wear-resistant materials, and the first piston 643 and the second piston 644 are wear-resistant. The high-toughness material can avoid the wear of the inner wall surface 613a of the hydraulic cylinder 64 of the intake rocker arm 6 made of light metal and the first piston 643 and the second piston 644, thereby effectively preventing a large amount of oil pressure leakage and avoiding oil pressure. The problem that the pistons 643, 644 cannot be pushed to the predetermined position occurs. Moreover, in the present invention, the partition wall 631 for partitioning the first driving oil passage 65 and the second driving oil passage 66 is integrally extended in the rocker shaft 63, so that it is unnecessary to additionally install another stopper separating member, thereby effectively reducing the number of parts. Quantity and exemption from additional assembly work. Furthermore, the foot support portions 612 and 622 of the high opening degree rocker arm 61 and the general opening degree rocker arm 62 are located between the shaft holes 611 and 621 and the pressing portion 625. The high opening degree rocker arm 61 and the general The through holes 613, 623 of the opening rocker arm 62 are located between the rollers 614, 624 and the shaft holes 611, 621, and are located above the center point connecting line A of the rollers 614, 624 and the shaft holes 611, 621. Further, the overall length of the intake rocker arm 6 can be suppressed, space is saved, and the cylinder head 33 can be prevented from overcoming the problem of insufficient space in a huge manner. And the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363 are coaxially disposed on the single cam shaft 336, so that the parts in the cylinder head 33 can be more compactly arranged, and the cylinder head 33 is prevented from being huge. The enlargement is beneficial to the space configuration of the cylinder head 33 on the whole vehicle.

In summary, the present invention, by the above configuration, can indeed improve the lack of use, and thereby achieve the purpose and effect of the claim, has met the practicality, novelty, and progressive requirements described in the invention patent, An application for an invention patent is filed.

The above is only the preferred embodiment of the present invention, and the scope of the invention is not limited thereto, that is, the simple equivalent changes and modifications made by the scope of the invention and the description of the invention are All remain within the scope of the invention patent.

1. . . engine

1a. . . Cylinder head

2. . . Valve valve

twenty one. . . High opening rocker

twenty two. . . General opening rocker

twenty three. . . spring

3. . . engine

31. . . Crankcase

311. . . Oil pump

312. . . Main oil supply channel

32. . . Cylinder body

33. . . Cylinder head

331. . . Intake

332. . . Intake valve

333. . . Exhaust gas

334. . . Vent

335. . . Camshaft seat

336. . . Camshaft

3361. . . Long intake cam

3362. . . Short intake cam

3363. . . Exhaust cam

337. . . Foot support mechanism

3371. . . Foot support

3372. . . Foot spring

3373. . . Foot support

33a. . . Valve spring

4. . . Oil control valve

41. . . Oil passage

5. . . Timing chain

51. . . Timing chain tensioner

6. . . Intake valve rocker

61. . . High opening rocker

611. . . Shaft hole

612. . . Foot support

613. . . Through hole

613a. . . Inner wall

614. . . Roller

62. . . General opening rocker

621. . . Shaft hole

622. . . Foot support

623. . . Through hole

624. . . Roller

625. . . Pressing part

6251. . . Gap adjustment

63. . . Rocker shaft

631. . . Partition wall

64. . . Hydraulic cylinder

641a‧641b. . . Plug cover

6411a‧6411b. . . Tab

642. . . Return spring

643. . . First piston

643a. . . Piston surface

6431. . . First groove

6432. . . Second groove

644. . . Second piston

644a. . . Piston surface

65. . . First drive oil circuit

66. . . Second drive oil circuit

7. . . Exhaust valve rocker

71. . . Pressing part

711. . . Gap adjustment

712. . . Shaft hole

72. . . Roller

73. . . Socket

74. . . Rocker shaft

A. . . The roller is connected to the center point of the shaft hole

Figure 1 is a schematic view of a conventional cylinder head.

Figure 2 is a schematic illustration of the engine cylinder head of the present invention.

Figure 3 is a schematic cross-sectional view of a portion of the cylinder head of the present invention.

Figure 4 is a schematic view showing the appearance of the cam shaft of the present invention.

Figure 5 is a schematic plan view of the cylinder head of the present invention.

Figure 6 is a schematic view of the rocker arm of the exhaust valve of the present invention.

Figure 7 is a schematic exploded view of the rocker arm of the intake valve of the present invention.

Figures 8 and 9 are embodiments of the invention.

33. . . Cylinder head

336. . . Camshaft

3361. . . Long intake cam

3362. . . Short intake cam

3363. . . Exhaust cam

6. . . Intake valve rocker

61. . . High opening rocker

613. . . Through hole

613a. . . Inner wall

614. . . Roller

62. . . General opening rocker

622. . . Foot support

623. . . Through hole

624. . . Roller

625. . . Pressing part

63. . . Rocker shaft

64. . . Hydraulic cylinder

641a‧641b. . . Plug cover

6411a‧6411b. . . Tab

642. . . spring

643. . . First piston

6431. . . First groove

6432. . . Second groove

644. . . Second piston

65, 66. . . First and second driving oil passages

7. . . Exhaust valve rocker

71. . . Pressing part

72. . . Roller

73. . . Socket

Claims (3)

An engine variable valve head mechanism having a cylinder head having an intake port and an intake valve, an exhaust port and an exhaust valve disposed between the intake port and the exhaust port There is a camshaft seat, and the camshaft seat is pivotally provided with a camshaft, wherein the camshaft is provided with a long intake cam, a short intake cam and an exhaust cam, and can push the intake air when the camshaft rotates. The valve rocker arm and the exhaust valve rocker arm actuate the intake valve and the exhaust valve; the intake valve rocker arm and the exhaust valve rocker arm are made of light metal alloy, and the above-mentioned intake valve rocker arm has a general opening degree rocker arm And a high opening degree rocker arm, wherein the general opening rocker arm is provided with a shaft hole, a through hole, a roller and a pressing portion, the high opening degree rocker arm has a shaft hole, a through hole and a roller, and the exhaust valve rocker arm has The shaft hole and the roller, the shaft hole of the general opening degree rocker arm and the high opening degree rocker arm are provided with a rocker arm shaft, the rocker arm shaft shaft is positioned on the cam shaft seat, and the first is connected with the oil control valve a driving oil passage and a second driving oil passage, wherein the rocker arm shaft is provided with a partition wall for separating the first driving oil passage and the second driving oil passage, and the general opening The roller of the rocker arm is in rolling contact with the short intake cam, and the pressing portion of the general opening rocker arm is in contact with the intake valve, and the roller of the high opening rocker arm is in rolling contact with the long intake cam. Wherein, the inner wall surface of the through hole of the general opening rocker arm and the through hole of the high opening degree rocker arm is wear-resistant material, and can be connected to form a hydraulic cylinder, and the above hydraulic cylinder is provided with wear resistance. a first piston and a second piston having a high toughness material, and a port communicating with the first oil passage and the second oil passage is respectively disposed at two ends of the hydraulic cylinder, and the first piston and the second piston can be borrowed Moved by the oil pressure output from the oil control valve, so when the engine is at high speed In the turning state, the first piston and the second piston are moved to a joint position of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm, and the high opening degree rocker arm and the general opening degree rocker arm are formed. The interlocking mode; when the engine is in the low speed running state, the first piston and the second piston are respectively separated from each other in the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm, and the high opening degree is obtained The rocker arm and the general opening rocker arm are in a respective mode of operation; the high-opening rocker arm and the main component of the general opening rocker arm and the exhaust valve rocker arm contain at least one light metal of aluminum or magnesium; the high opening rocker arm The wear-resistant material of the inner wall surface of the through hole of the through hole and the general opening rocker arm is high carbon steel; the high toughness of the first piston and the second piston with high wear resistance is tool steel; the high opening degree rocker arm and the general The main component of the opening rocker arm and the exhaust valve rocker arm contains at least one kind of light metal of aluminum or magnesium; the wear-resistant material of the inner wall surface of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm is high carbon steel The first piston and the second piston have high wear resistance and are made of tool steel; the high opening rocker arm The through hole of the hole and the general opening rocker arm is located between the roller and the shaft hole, and is located above the line connecting the center point of the roller and the shaft hole; the two ends of the hydraulic cylinder are respectively sealed with a plug cover, and the plug cover is facing a protruding post is protruded on the inner side of the hydraulic cylinder; the through hole of the general opening rocker is provided with a return spring, the return spring is in contact with the first piston, and the first piston is provided with a first groove and a second groove The first groove is matched with the boss of the plug cover; the cylinder head is further provided with a foot support mechanism that abuts the high opening degree rocker arm and the general opening degree rocker arm, and the foot support mechanism includes a foot support tube, a foot support spring and a foot support hole for receiving the foot support tube and the foot spring; the cam shaft is a single cam shaft coaxially provided with a long intake cam, a short intake cam and an exhaust cam. The variable valve head mechanism of the engine of claim 1, wherein the high opening rocker arm and the general opening rocker arm are further provided with a foot support portion, and the foot support portion is a foot of the foot support mechanism The struts are in contact. The variable valve head mechanism of the engine of claim 2, wherein the high opening degree rocker arm and the foot portion of the general opening degree rocker arm are located between the shaft hole and the pressing portion.