Cam groove type engine valve mechanism and engine

Abstract

The invention belongs to the technical field of engines, and particularly relates to a cam groove type engine valve mechanism which comprises a cylinder head body. The cam structure is in transmission connection with the crankshaft, the cam structure is rotationally installed on the cylinder head body, the cam structure comprises a rotating disc and a cam auxiliary disc protruding out of the rotating disc, a groove is formed in the rotating disc, the outer contour of the groove is matched with the outer contour of the rotating disc, and the groove is located on the outer side of the groove; the air valve is axially mounted on the cylinder head body in a sliding manner, a first mounting seat is transversely arranged on the air valve, a first bearing and a second bearing are rotatably mounted on the first mounting seat, and the first bearing and the second bearing are coaxially arranged; the first bearing is attached to the outer side wall of the groove, and the second bearing is attached to the outer edge of the cam auxiliary disc. The invention aims to solve the problem that parts of the valve mechanism fly off when the rotating speed of an engine is higher and the difference between the actual movement rule of the valve and the ideal movement of the valve is more obvious and serious due to the structural defects of the existing valve mechanism.

Description

Technical Field

[0001] The invention belongs to the technical field of engines, and in particular relates to a cam groove type engine valve mechanism and an engine. Background Art

[0002] The valve mechanism is divided into two parts: the valve group and the valve transmission group, and is an important part of the engine.

[0003] Its basic function is to open and close the intake and exhaust valves in a timely manner according to the requirements of the working cycle and ignition sequence in each cylinder of the engine, so that fresh air can enter the cylinder in time and exhaust gas can be discharged from the cylinder.

[0004] The valve distribution structure is used to realize the opening and closing of the valve. In the related art, the valve distribution structure mainly relies on the cam, tappet, push rod, rocker arm and valve spring seat to realize the opening and closing of the valve, that is, the cam is used to press the valve down to make the valve in the open state, and then the return spring resets the valve to make the valve closed.

[0005] However, due to the elastic deformation of the return spring in the valve train, there is a certain difference between the actual movement of the valve at the end of the transmission chain and the ideal movement of the valve. The higher the engine speed, the more obvious the difference between the actual movement of the valve and the ideal movement of the valve. In serious cases, it will cause the valve train parts to fly off. Summary of the invention

[0006] The purpose of the present invention is to provide a cam groove type engine valve mechanism to solve the problem that the difference between the actual movement law of the valve and the ideal movement of the valve becomes more obvious when the engine speed is higher due to the structural defects of the existing valve mechanism. In serious cases, the valve mechanism parts may fly off.

[0007] In order to achieve the above technical objectives, the technical solution adopted by the present invention is as follows:

[0008] A cam groove type engine valve mechanism, comprising:

[0009] Cylinder head body;

[0010] A cam structure connected to the crankshaft driving, the cam structure is rotatably mounted on the cylinder head body, the cam structure comprises a cam sub-disc protruding from a rotating disk, a groove is formed on the rotating disk, the outer contour of the groove matches the outer contour of the rotating disk, and is located outside the groove;

[0011] A valve, wherein the valve is axially slidably mounted on the cylinder head body, a first mounting seat is transversely arranged on the valve, a first bearing and a second bearing are rotatably mounted on the first mounting seat, and the first bearing and the second bearing are coaxially arranged;

[0012] The first bearing is in contact with the outer side wall of the groove, and the second bearing is in contact with the outer edge of the cam sub-disk.

[0013] It is further defined that a guide cylinder is provided on the cylinder head body;

[0014] A cylinder seat is installed on the air valve, and the cylinder seat is slidably installed in the guide cylinder.

[0015] Such a structural design achieves the technical purpose of axially sliding installation of the valve on the cylinder head body through the mutual cooperation of the guide cylinder and the cylinder seat. It has a simple structure, is easy to install, and is highly practical.

[0016] It is further defined that the valve is inserted into the cartridge seat, the first mounting seat is fixedly mounted on the cartridge seat, a first fixing mechanism is mounted above the valve in the cartridge seat, and a first elastic structure is mounted between the first fixing mechanism and the valve;

[0017] A limiting ring is installed on the lower end surface of the cylinder seat, a limiting mechanism is installed above the limiting ring on the valve, and a second elastic structure is installed between the limiting ring and the limiting mechanism.

[0018] Such a structural design enables the valve to have a certain degree of freedom relative to the first mounting seat through the mutual cooperation between the cartridge seat and the valve, and enables the valve to have a certain degree of freedom of axial movement relative to the cartridge seat on the basis of being able to move synchronously with the cartridge seat in cooperation with the first elastic structure and the second elastic structure;

[0019] Thus, before the cylinder seat reaches the top dead center, the valve contacts the valve seat first. With the further rotation of the cam structure, the valve has a tendency to move upward synchronously under the action of the cylinder seat. This tendency is applied to the valve seat to form a seating force, thereby completing the sealing of the valve to the valve seat.

[0020] Avoid the problem of insufficient valve seating force caused by rigid contact between the valve and cam structure, which in turn affects the sealing between the valve and the valve seat.

[0021] It is further defined that the first mounting seat is located below the central axis of the cam structure;

[0022] A piston is slidably mounted in the cylinder seat between the first fixed structure and the valve;

[0023] The cartridge seat forms a cavity between the first fixed structure and the piston, the first elastic structure is located between the first fixed structure and the piston, and a connecting hole communicating with the cavity is opened on the side wall of the cartridge seat;

[0024] The guide cylinder is provided with an oil inlet passage and an oil drain passage, both of which are connected to the inner wall of the guide cylinder. The oil inlet passage is located above the oil drain passage, the oil inlet passage is connected to the hydraulic pump, and the oil drain passage is connected to the oil tank.

[0025] Such a structural design, through the setting of the oil inlet channel and the oil drain channel, cooperates with the high-pressure oil source formed by the external hydraulic oil under the action of the hydraulic pump, so that the oil pressure in the oil inlet channel is greater than the oil pressure in the cavity. Before the cylinder seat moves downward from the top dead center to the connection between the oil drain channel and the cavity, and before the cavity is separated from the connection with the oil drain channel to the connection between the oil inlet channel and the cavity, based on the incompressible property of oil, the cylinder seat, valve and piston can be regarded as a whole, that is, the cylinder seat, valve and piston are rigidly connected at this time by using oil, so as to avoid the problem of low accuracy of the opening time caused by the axial sliding freedom between the valve and the cylinder seat during the movement of the valve driven by the cylinder seat, thereby improving the control accuracy of the valve opening time;

[0026] At the same time, by placing the first mounting seat below the central axis of the cam structure, relative to the technical solution in which the first mounting seat is located above the central axis of the cam structure, the first mounting seat is closer to the lower end of the valve. When the valve and the cylinder seat move, the swing amplitude of the lower end of the valve is smaller, the operation is more stable, and the practicality is stronger.

[0027] It is further defined that the outer wall of the cartridge seat is also laterally provided with a second mounting seat, and a third bearing is rotatably mounted on the second mounting seat;

[0028] A guide seat is vertically fixed on the guide cylinder, and the third bearing is slidably installed in the guide seat.

[0029] Such a structural design limits the rotational freedom of the cylinder seat through the mutual cooperation between the third bearing on the second mounting seat and the guide seat, thereby avoiding the problem of the first bearing and the second bearing being out of contact with the cam structure during operation, thereby causing a decrease in control accuracy. It is highly practical.

[0030] It is further defined that the oil drain passage is communicated with the guide seat and is located above the third bearing.

[0031] Such a structural design, through the setting of the oil drain channel, introduces oil into the guide seat to lubricate the third bearing, which can reduce the friction between the third bearing and the guide seat, making the rolling of the third bearing smoother and more practical.

[0032] It is further defined that the cylinder seat is provided with a drainage channel at a position corresponding to the oil leakage channel;

[0033] The upper end surface of the limiting ring is provided with an oil retaining ring;

[0034] The limit ring, the oil retaining ring and the inner wall of the cylinder seat together form an oil storage cavity, and the drainage channel is connected to the oil storage cavity;

[0035] The first mounting seat and / or the second mounting seat is provided with a secondary channel communicated with the oil storage cavity, and the secondary channel is used for lubricating the first mounting seat and / or the second mounting seat.

[0036] Such a structural design, through the setting of the drainage channel, guides part of the oil in the oil leakage channel to the oil storage chamber, and then lubricates the first mounting seat and / or the second mounting seat on the inside through the secondary channel, thereby further reducing the friction force, making the rolling of the bearing on the first mounting seat and / or the second mounting seat smoother and more practical.

[0037] It is further defined that the oil retaining ring is also provided with an overflow hole.

[0038] Such a structural design, through the setting of the overflow hole, allows the excess oil in the oil storage chamber to flow into the oil tank from the overflow hole instead of accumulating in the oil storage chamber, and is highly practical.

[0039] It is further defined that the oil inlet passage and / or the oil drain passage are inclined inwardly from top to bottom near one end of the cylinder seat.

[0040] Such a structural design, through the inclined setting of the oil inlet channel and / or the oil drain channel, ensures that even if a small amount of external air enters the oil inlet channel and / or the oil drain channel, based on the characteristic that the density of oil is greater than the density of air, the air can be stored in the upper part of the oil inlet channel and / or the oil drain channel, and will not directly enter the cavity to affect the control accuracy. The structural design is highly practical.

[0041] An engine comprises the above-mentioned cam groove type engine valve mechanism.

[0042] The invention adopting the above technical solution has the following advantages:

[0043] 1. Through the fit of the first bearing and the outer wall of the groove, and the fit of the second bearing and the outer edge of the cam sub-disk, the rotation of the cam structure is used to directly drive the axial movement of the valve, thereby realizing the opening and closing of the valve, without the need to configure a reset spring for driving the valve to reset, thus avoiding the problem of movement difference of the engine at high speed caused by the elastic deformation of the reset spring in the valve structure;

[0044] At the same time, the first bearing and the second bearing arranged coaxially are respectively fitted with the groove and the cam sub-disk at different heights relative to the cam structure, so as to avoid the bearing contacting different components in two different directions at the same time, thereby causing the bearing to be unable to rotate, and the practicability is strong;

[0045] 2. The valve has a certain degree of freedom relative to the first mounting seat through the mutual cooperation between the cartridge seat and the valve. The valve has a certain degree of freedom of axial movement relative to the cartridge seat in cooperation with the first elastic structure and the second elastic structure. The valve can move synchronously with the cartridge seat and has a certain degree of freedom of axial movement relative to the cartridge seat.

[0046] Thus, before the cylinder seat reaches the top dead center, the valve contacts the valve seat first. With the further rotation of the cam structure, the valve has a tendency to move upward synchronously under the action of the cylinder seat. This tendency is applied to the valve seat to form a seating force, thereby completing the sealing of the valve to the valve seat.

[0047] Avoid the problem of insufficient valve seating force caused by rigid contact between the valve and cam structure, which in turn affects the sealing between the valve and the valve seat.

[0048] 3. Through the setting of the oil inlet and oil drain passages, in conjunction with the high-pressure oil source formed by the external hydraulic oil under the action of the hydraulic pump, the oil pressure in the oil inlet passage is greater than the oil pressure in the cavity. Before the cylinder seat moves downward from the top dead center to the connection between the oil drain passage and the cavity, and before the cavity is separated from the connection with the oil drain passage to the connection between the oil inlet and the cavity, based on the incompressible property of oil, the cylinder seat, valve and piston can be regarded as a whole, that is, the cylinder seat, valve and piston are rigidly connected at this time by using oil, so as to avoid the problem of low accuracy of the opening time caused by the axial sliding freedom between the valve and the cylinder seat during the movement of the valve driven by the cylinder seat, thereby improving the control accuracy of the valve opening time;

[0049] At the same time, by placing the first mounting seat below the central axis of the cam structure, compared with the technical solution in which the first mounting seat is located above the central axis of the cam structure, the distance between the first mounting seat and the lower end of the valve is closer, and when the valve and the cylinder seat move, the swing amplitude of the lower end of the valve is smaller, the operation is more stable, and the practicality is stronger;

[0050] 4. The third bearing on the second mounting seat cooperates with the guide seat to limit the rotational freedom of the cylinder seat, thereby preventing the first bearing and the second bearing from being out of contact with the cam structure during operation, thereby causing a decrease in control accuracy, and the practicability is relatively strong;

[0051] 5. By setting up the oil drain channel, the oil is introduced into the guide seat to lubricate the third bearing, which can reduce the friction between the third bearing and the guide seat, making the rolling of the third bearing smoother and more practical;

[0052] 6. Through the setting of the drainage channel, part of the oil in the oil drain channel is guided to the oil storage chamber, and then through the auxiliary channel, the first mounting seat and / or the second mounting seat are lubricated on the inner side, so as to further reduce the friction force, so that the rolling of the bearing on the first mounting seat and / or the second mounting seat is smoother, and the practicality is strong;

[0053] 7. By setting the oil inlet and / or oil drain passage inclined, even if a small amount of outside air enters the oil inlet and / or oil drain passage, the air can be stored in the upper part of the oil inlet and / or oil drain passage due to the characteristic that the density of oil is greater than the density of air, and will not directly enter the cavity, thereby affecting the control accuracy, and the practicality is strong. BRIEF DESCRIPTION OF THE DRAWINGS

[0054] The present invention can be further illustrated by the non-limiting examples given in the accompanying drawings;

[0055] Figure 1 It is a structural schematic diagram of a cam groove type engine valve mechanism and an engine embodiment of the present invention;

[0056] Figure 2 The structure diagram of a cam groove type engine valve mechanism and some parts in the engine embodiment of the present invention is shown in FIG. Figure 1 ;

[0057] Figure 3 The structure diagram of a cam groove type engine valve mechanism and some parts in the engine embodiment of the present invention is shown in FIG. Figure 2 ;

[0058] Figure 4 It is a structural schematic diagram of a cam groove type engine valve mechanism and a cam structure part in an engine embodiment of the present invention;

[0059] Figure 5 It is a cross-sectional structural schematic diagram of a cam groove type engine valve mechanism and an engine embodiment of the present invention;

[0060] Figure 6 for Figure 5 A schematic diagram of the enlarged structure at A in the middle;

[0061] Figure 7 It is a cross-sectional structural schematic diagram of a cam groove type engine valve mechanism and a guide cylinder part in an engine embodiment of the present invention;

[0062] Figure 8 It is a cross-sectional structural schematic diagram of a cam groove type engine valve mechanism and a cylinder seat part in an engine embodiment of the present invention;

[0063] The main component symbols are described as follows:

[0064] Cylinder head body 1, oil inlet passage 101, oil drain passage 102, drainage passage 103,

[0065] Guide cylinder 11, guide seat 110, guide tube 12, valve seat 13,

[0066] Cam structure 2, rotating disk 20, groove 21, cam sub-disk 22,

[0067] Valve 3, first bearing 31, second bearing 32, third bearing 33, second mounting seat 330,

[0068] The cartridge seat 4, the first elastic structure 40, the first fixing mechanism 401,

[0069] Piston 41, cavity 410,

[0070] The connecting hole 42, the first annular groove 421, the second annular groove 422,

[0071] Limiting ring 43, oil retaining ring 431, overflow hole 432, auxiliary channel 433,

[0072] The limiting seat 5 , the second elastic structure 50 , and the second fixing structure 501 . DETAILED DESCRIPTION

[0073] The present invention will be described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that in the drawings or descriptions of the specification, similar or identical parts use the same figure numbers, and the implementation methods not shown or described in the drawings are forms known to ordinary technicians in the relevant technical field. In addition, the directional terms mentioned in the embodiments, such as "upper", "lower", "top", "bottom", "left", "right", "front", "back", etc., are only referenced to the directions of the drawings and are not used to limit the scope of protection of the present invention.

[0074] like Figures 1 to 8 As shown, a cam groove type engine valve mechanism of the present invention comprises:

[0075] Cylinder head body 1;

[0076] A cam structure 2 connected to the crankshaft driving, the cam structure 2 is rotatably mounted on the cylinder head body 1, the cam structure 2 comprises a rotating disk 20, a cam sub-disk 22 protruding from the rotating disk 20, a groove 21 is formed on the rotating disk 20, the outer contour of the groove 21 matches the outer contour of the rotating disk 20, and is located outside the groove 21;

[0077] The valve 3 is axially slidably mounted on the cylinder head body 1. A first mounting seat is transversely arranged on the valve 3. A first bearing 31 and a second bearing 32 are rotatably mounted on the first mounting seat. The first bearing 31 and the second bearing 32 are coaxially arranged.

[0078] The first bearing 31 is in contact with the outer side wall of the groove 21 , and the second bearing 32 is in contact with the outer edge of the cam sub-disk 22 .

[0079] A guide cylinder 11 is provided on the cylinder head body 1;

[0080] A cylinder seat 4 is mounted on the valve 3 , and the cylinder seat 4 is slidably mounted in the guide cylinder 11 .

[0081] In fact, according to actual conditions, it is also possible to choose to install a linear bearing on the cylinder head body 1, and complete the axial sliding installation through the cooperation between the linear bearing and the valve 3. This embodiment achieves the technical purpose of axially sliding installation of the valve 3 on the cylinder head body 1 through the cooperation between the guide cylinder 11 and the cylinder seat 4. It has a simple structure, is easy to install, and is highly practical.

[0082] A guide tube 12 is installed on the cylinder head body 1 , and the valve 3 is slidably installed in the guide tube 12 .

[0083] Through the mutual cooperation between the valve 3 and the guide tube 12, the stability of the sliding installation between the valve 3 and the cylinder head body 1 is further enhanced, and the practicality is strong.

[0084] The valve 3 is inserted into the cartridge seat 4, the first mounting seat is fixedly mounted on the cartridge seat 4, a first fixing mechanism 401 is mounted above the valve 3 in the cartridge seat 4, and a first elastic structure 40 is mounted between the first fixing mechanism 401 and the valve 3;

[0085] A limit ring 43 is installed on the lower end surface of the cylinder seat 4, a limit mechanism is installed above the limit ring 43 on the valve 3, and a second elastic structure 50 is installed between the limit ring 43 and the limit mechanism.

[0086] In fact, according to actual conditions, the first mounting seat can be directly fixed on the valve 3, and the cam structure 2 can directly drive the valve 3 to slide up and down. In this embodiment, the valve 3 has a certain degree of freedom relative to the first mounting seat through the mutual cooperation between the cartridge seat 4 and the valve 3. With the first elastic structure 40 and the second elastic structure 50, the valve 3 can move synchronously with the cartridge seat 4, and the valve 3 also has a certain degree of freedom of axial movement relative to the cartridge seat 4.

[0087] Thus, before the cylinder seat 4 reaches the top dead center, the valve 3 first contacts the valve seat 13. As the cam structure 2 further rotates, the valve 3 has a synchronous upward trend under the action of the cylinder seat 4. This trend is applied to the valve seat 13 to form a seating force, thereby completing the sealing of the valve 3 to the valve seat 13.

[0088] This avoids the problem of insufficient seating force of the valve 3 due to the rigid contact between the valve 3 and the cam structure 2, thereby affecting the sealing between the valve 3 and the valve seat 13.

[0089] The first mounting seat is located below the central axis of the cam structure 2;

[0090] A piston 41 is slidably mounted in the cylinder seat 4 between the first fixed structure 401 and the valve 3;

[0091] The cartridge seat 4 forms a cavity 410 between the first fixed structure 401 and the piston 41. The first elastic structure 40 is located between the first fixed structure 401 and the piston 41. The side wall of the cartridge seat 4 is provided with a connecting hole 42 connected with the cavity 410.

[0092] The guide cylinder 11 is provided with an oil inlet passage 101 and an oil drain passage 102, both of which are connected to the inner wall of the guide cylinder 11, the oil inlet passage 101 is located above the oil drain passage 102, the oil inlet passage 101 is connected to the hydraulic pump, and the oil drain passage 102 is connected to the oil tank.

[0093] In fact, according to actual conditions, the first mounting seat can also be placed above the central axis of the cam structure 2, and the oil inlet passage 101 can be placed below the oil drain passage 102. In this embodiment, the oil inlet passage 101 and the oil drain passage 102 are arranged, and the high-pressure oil source formed by the external hydraulic oil under the action of the hydraulic pump is matched, so that the oil pressure in the oil inlet passage 101 is greater than the oil pressure in the cavity 410. Before the cylinder seat 4 moves downward from the top dead center to the connection between the oil drain passage 102 and the cavity 410, and before the cavity 410 is separated from the connection with the oil drain passage 102 to the connection between the oil inlet passage 101 and the cavity 410, based on the incompressible property of oil, the cylinder seat 4 and the piston 41 can be regarded as a whole, that is, the cylinder seat 4 and the piston 41 are rigidly connected at this time by using oil, so as to avoid the problem of low accuracy of the opening time caused by the axial sliding freedom between the valve 3 and the cylinder seat 4 during the movement of the valve 3 driven by the cylinder seat 4, thereby improving the control accuracy of the opening time of the valve 3.

[0094] At the same time, by placing the first mounting seat below the central axis of the cam structure 2, relative to the technical solution in which the first mounting seat is located above the central axis of the cam structure 2, the distance between the first mounting seat and the lower end of the valve 3 is closer, and when the valve 3 and the cylinder seat 4 move, the swing amplitude of the lower end of the valve 3 is smaller, the operation is more stable, and the practicality is stronger.

[0095] A one-way valve is provided in the oil inlet passage 101 .

[0096] By setting the one-way valve in the oil inlet passage 101, after the cam structure 2 drives the cylinder seat 4 to pass the top dead center, and before the cylinder seat 4 descends to the connecting hole 42 to disconnect from the oil inlet passage 101, the cylinder seat 4 has a tendency to move downward relative to the valve 3, that is, when the volume of the cavity 410 tends to decrease, the problem of excessive instantaneous oil pressure in the cavity 410 and the backflow of oil in the oil inlet passage 101 caused by the oil pressure being too high can be avoided.

[0097] The outer wall of the cylinder seat 4 is also laterally provided with a second mounting seat 330, and a third bearing 33 is rotatably mounted on the second mounting seat 330;

[0098] A guide seat 110 is vertically fixed on the guide cylinder 11 , and the third bearing 33 is slidably installed in the guide seat 110 .

[0099] Through the mutual cooperation between the third bearing 33 on the second mounting seat 330 and the guide seat 110, the rotational freedom of the cylinder seat 4 is restricted, so as to avoid the first bearing 31 and the second bearing 32 being out of contact with the cam structure 2 during operation, thereby causing a decrease in control accuracy, and the practicability is strong.

[0100] The oil drain passage 102 is communicated with the guide seat 110 and is located above the third bearing 33 .

[0101] By setting the oil drain channel 102, oil is introduced into the guide seat 110 to lubricate the third bearing 33, which can reduce the friction between the third bearing 33 and the guide seat 110, making the rolling of the third bearing 33 smoother and more practical.

[0102] The cylinder seat 4 is provided with a drainage channel 103 at a position corresponding to the oil drain channel 102;

[0103] An oil retaining ring 431 is provided on the upper end surface of the limiting ring 43;

[0104] The limiting ring 43, the oil retaining ring 431 and the inner wall of the cylinder seat 4 together form an oil storage cavity, and the drainage channel 103 is connected to the oil storage cavity;

[0105] A secondary passage 433 communicating with the oil storage cavity is formed on the first mounting seat and / or the second mounting seat 330 , and the secondary passage 433 is used to lubricate the first mounting seat and / or the second mounting seat 330 .

[0106] Through the setting of the drainage channel 103, part of the oil in the oil drain channel 102 is guided to the oil storage chamber, and then through the auxiliary channel 433, the first mounting seat and / or the second mounting seat 330 are lubricated on the inner side, further reducing the friction, so that the bearing on the first mounting seat and / or the second mounting seat 330 rolls more smoothly, which is more practical.

[0107] The oil retaining ring 431 is also provided with an overflow hole 432 .

[0108] By setting the overflow hole 432, the excess oil in the oil storage chamber can flow into the oil tank from the overflow hole 432, and will not accumulate in the oil storage chamber, which is more practical.

[0109] The oil inlet passage 101 and / or the oil drain passage 102 are inclined inward from top to bottom near one end of the cylinder seat 4 .

[0110] In fact, the oil inlet passage 101 and / or the oil leakage passage 102 may be horizontally arranged according to actual conditions. In this embodiment, the oil inlet passage 101 and / or the oil leakage passage 102 are inclined so that even if a small amount of external air enters the oil inlet passage 101 and / or the oil leakage passage 102, based on the characteristic that the density of oil is greater than the density of air, the air can be stored in the upper part of the oil inlet passage 101 and / or the oil leakage passage 102, and will not directly enter the cavity 410, thereby affecting the accuracy of control, and the practicality is strong.

[0111] There are multiple communicating holes 42, and the multiple communicating holes 42 are arranged circumferentially along the central axis of the cylinder seat 4;

[0112] The inner wall of the guide cylinder 11 is also provided with a first annular groove 421 communicating with the oil inlet passage 101;

[0113] The inner wall of the guide cylinder 11 is further provided with a second annular groove 422 which is in communication with the oil drain passage 102 .

[0114] In fact, according to actual conditions, only one connecting hole 42 corresponding to the oil inlet channel 101 and the oil drain channel 102 can be set. In this embodiment, multiple connecting holes 42 are set up, and the first annular groove 421 and the second annular groove 422 are matched to make it easier for oil to enter and exit the cavity 410, which is more practical.

[0115] The first elastic structure 40 and / or the second elastic structure 50 is a compression spring.

[0116] In fact, according to actual conditions, an elastic structure such as a disc spring can be selected as the first elastic structure 40 and / or the second elastic structure 50. This embodiment uses a compression spring as the first elastic structure 40 and / or the second elastic structure 50, which has a simple structure, is easy to install, and is highly practical.

[0117] The limiting mechanism comprises a limiting seat 5 sleeved on the valve 3 and a second fixing structure 501;

[0118] The upper end surface of the limiting seat 5 is provided with a conical groove;

[0119] The second fixing structure 501 is a semicircular locking clamp with two outer walls inclined inward from top to bottom;

[0120] The inner wall of the semicircular locking clamp is provided with a half ring, and the outer wall of the valve 3 is provided with a second ring groove.

[0121] In fact, according to actual conditions, it is also possible to choose a method such as directly screwing the limit mechanism onto the valve 3 to complete the restriction of the upward movement freedom of the limit mechanism relative to the valve 3. This embodiment limits the upward movement freedom of the limit mechanism relative to the valve 3 through the mutual cooperation of the semicircular locking clamp, the conical groove, the half ring and the second ring groove, and then cooperates with the second elastic structure 50 to form a support between the valve 3 and the cylinder seat 4. It has a simple structure, is easy to install, and is highly practical.

[0122] An engine comprises the above-mentioned cam groove type engine valve mechanism.

[0123] In this embodiment, when in use, the cam structure 2 rotates along with the crankshaft, driving the rotating disk 20, the groove 21 and the cam sub-disk 22 to rotate;

[0124] When the first bearing 31 is fitted with the outer wall of the groove 21 which is closer to the rotation center of the cam structure 2, and the second bearing 32 is fitted with the outer edge of the cam sub-disk 22 which is closer to the rotation center of the cam structure 2, that is, when the cylinder seat 4 is at the top dead center, the valve 3 is abutted against the valve seat 13, and the valve 3 is in a closed state. At this time, the connecting hole 42 is connected with the oil inlet passage 101 through the first annular groove 421, and the second elastic structure 50 forms an upward thrust on the valve 3 through the limit seat 5, overcoming the prestress of the first elastic structure 40, forming a seating force of the valve 3 on the valve seat 13, and completing the sealing between the valve 3 and the valve seat 13, as shown in FIG. Figure 1-3 and Figure 5-Figure 6 As shown;

[0125] The cam structure 2 continues to rotate until the first bearing 31 is separated from the edge of the groove 21 closer to the rotation center of the cam structure 2 and the second bearing 32 is separated from the edge of the cam sub-disk 22 closer to the rotation center of the cam structure 2, and starts to drive the cylinder seat 4 to move downward relative to the cylinder head body 1 until the communication hole 42 is separated from the communication with the oil inlet passage 101;

[0126] During this process, the cartridge seat 4 has a tendency to move downward relative to the valve 3, that is, the volume of the cavity 410 tends to decrease, and because the external hydraulic oil forms a high-pressure oil source under the action of the hydraulic pump, the oil pressure in the oil inlet passage 101 is greater than the oil pressure in the cavity 410, and a one-way valve is provided in the oil inlet passage 101 to prevent the oil in the cavity 410 from entering the oil inlet passage 101 through the connecting hole 42. Based on the incompressible property of the oil, at this time, the cartridge seat 4 and the piston 41 can be regarded as a whole, that is, the cartridge seat 4 and the piston 41 are rigidly connected by the oil, and the upper end of the valve 3 is against the piston 41. During this process, the valve 3 moves downward synchronously with the cartridge seat 4, thereby accurately completing the opening of the valve 3.

[0127] The cam structure 2 continues to rotate, and the cartridge seat 4 continues to move downward. After the communication hole 42 is disconnected from the oil inlet passage 101, until the communication hole 42 is connected to the oil drain passage 102, the cavity 410 is in a closed state. At this time, based on the incompressible property of oil, the cartridge seat 4 and the piston 41 can be regarded as a whole, that is, the cartridge seat 4 and the piston 41 are rigidly connected by the oil. In this process, the piston 41 is pressed against the upper end of the valve 3, so that the valve 3 moves downward synchronously with the cartridge seat 4, thereby further increasing the opening degree of the valve 3.

[0128] The cam structure 2 continues to rotate, and the cartridge seat 4 continues to move downward until the communicating hole 42 is connected to the oil drain passage 102, and the rigid connection is destroyed, so that the piston 41 has the freedom to move upward relative to the cartridge seat 4. At this time, the stopper seat 5, under the action of the second elastic structure 50, drives the valve 3 to move upward relative to the cartridge seat 4 until the cartridge seat 4 rises again to the point where the communicating hole 42 is disconnected from the oil drain passage 102.

[0129] In this process, the second elastic structure 50 is used to drive the valve 3 to move upward relative to the cartridge seat 4, so as to prepare a displacement for the cartridge seat 4 to move upward relative to the valve 3 after the valve is seated next time.

[0130] At the same time, the upward movement of the valve 3 relative to the cylinder seat 4 pushes the piston 41 to move toward the first fixing mechanism 401, so that the oil in the cavity 410 enters the oil drain channel 102 through the connecting hole 42, completing the oil drain;

[0131] After the oil enters the oil drain passage 102 from the cavity 410 , it flows out from the lower end of the oil drain passage 102 , and part of the oil drips directly onto the third bearing 33 to lubricate the third bearing 33 ;

[0132] Some of the oil is received by the drainage channel 103, and some of the oil in the oil drain channel 102 is guided to the oil storage chamber, and then through the auxiliary channel 433, the first mounting seat and / or the second mounting seat 330 are lubricated on the inside;

[0133] The excess oil in the oil storage chamber flows into the oil tank from the overflow hole 432;

[0134] The cam structure 2 continues to rotate. After the cylinder seat 4 rises again to the point where the connecting hole 42 is disconnected from the oil drain passage 102, and before the connecting hole 42 is connected to the oil drain passage 102 again, the cavity 410 is in a closed state. Based on the incompressible property of oil, the cylinder seat 4 and the piston 41 can be regarded as a whole, and then the second elastic mechanism 50 supports the limit seat 5, driving the valve 3 to move upward.

[0135] In the process from when the valve 3 starts to contact with the valve seat 13 to when the cylinder seat 4 reaches the top dead center, the cylinder seat 4 continues to move upward relative to the cylinder head body 1 under the action of the cam structure 2, and the valve 3 cannot move due to the contact between the valve 3 and the valve seat 13, and the second elastic structure 50 forms an upward thrust on the limit seat 5, and then forms a seating force of the valve 3 on the valve seat 13 through the valve 3, thereby completing the sealing between the valve 3 and the valve seat 13;

[0136] After the valve 3 contacts the valve seat 13 again, the connecting hole 42 is connected with the oil inlet passage 101 again. Due to the upward movement of the cylinder seat 4 relative to the valve seat 13, the valve 3 is separated from the abutment against the piston 41. The hydraulic pump injects oil into the cavity 410 through the oil inlet passage 101, so that the piston 41 abuts against the upper end of the valve 3 again until the cylinder seat 4 reaches the top dead center.

[0137] The above is a detailed introduction to a cam groove type engine valve mechanism and an engine provided by the present invention. The description of the specific embodiment is only used to help understand the method and core idea of ​​the present invention. It should be pointed out that for ordinary technicians in this technical field, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A cam groove type engine valve mechanism, characterized in that: include: Cylinder head body (1); A cam structure (2) drivingly connected to the crankshaft, the cam structure (2) being rotatably mounted on the cylinder head body (1), the cam structure (2) comprising a rotating disk (20) and a cam sub-disk (22) protruding from the rotating disk (20), the rotating disk (20) being provided with a groove (21), the outer contour of the groove (21) matching the outer contour of the rotating disk (20) and being located outside the groove (21); A valve (3), the valve (3) being axially slidably mounted on the cylinder head body (1), the valve (3) being laterally provided with a first mounting seat, the first mounting seat being rotatably provided with a first bearing (31) and a second bearing (32), the first bearing (31) and the second bearing (32) being coaxially arranged; The first bearing (31) is in contact with the outer side wall of the groove (21), and the second bearing (32) is in contact with the outer edge of the cam sub-disk (22).

2. A cam groove type engine valve train according to claim 1, characterized in that: The cylinder head body (1) is provided with a guide cylinder (11); A cylinder seat (4) is mounted on the valve (3), and the cylinder seat (4) is slidably mounted in the guide cylinder (11).

3. A cam groove type engine valve train according to claim 2, characterized in that: The air valve (3) is inserted into the cylinder seat (4), the first mounting seat is fixedly mounted on the cylinder seat (4), a first fixing mechanism (401) is mounted above the air valve (3) in the cylinder seat (4), and a first elastic structure (40) is mounted between the first fixing mechanism (401) and the air valve (3); A limiting ring (43) is installed on the lower end surface of the cylinder seat (4), a limiting mechanism is installed on the valve (3) above the limiting ring (43), and a second elastic structure (50) is installed between the limiting ring (43) and the limiting mechanism.

4. A cam groove type engine valve train according to claim 3, characterized in that: The first mounting seat is located below the central axis of the cam structure (2); A piston (41) is slidably mounted in the cylinder seat (4) between the first fixed structure (401) and the valve (3); The cartridge seat (4) forms a cavity (410) between the first fixed structure (401) and the piston (41); the first elastic structure (40) is located between the first fixed structure (401) and the piston (41); and a communication hole (42) communicating with the cavity (410) is formed on a side wall of the cartridge seat (4); The guide cylinder (11) is provided with an oil inlet passage (101) and an oil drain passage (102); the oil inlet passage (101) and the oil drain passage (102) are both in communication with the inner wall of the guide cylinder (11); the oil inlet passage (101) is located above the oil drain passage (102); the oil inlet passage (101) is in communication with a hydraulic pump; and the oil drain passage (102) is in communication with an oil tank.

5. A cam groove type engine valve train according to claim 4, characterized in that: A second mounting seat (330) is also laterally arranged on the outer wall of the cylinder seat (4), and a third bearing (33) is rotatably mounted on the second mounting seat (330); A guide seat (110) is vertically fixedly provided on the guide cylinder (11), and the third bearing (33) is slidably mounted in the guide seat (110).

6. A cam groove type engine valve train according to claim 5, characterized in that: The oil drain channel (102) is communicated with the guide seat (110) and is located above the third bearing (33).

7. A cam groove type engine valve train according to claim 6, characterized in that: The cylinder seat (4) is provided with a drainage channel (103) at a position corresponding to the oil leakage channel (102); An oil retaining ring (431) is provided on the upper end surface of the limiting ring (43); The limiting ring (43), the oil retaining ring (431) and the inner wall of the cylinder seat (4) together form an oil storage cavity, and the drainage channel (103) is in communication with the oil storage cavity; The first mounting seat and / or the second mounting seat (330) is provided with a secondary channel (433) which is in communication with the oil storage cavity, and the secondary channel (433) is used to lubricate the first mounting seat and / or the second mounting seat (330).

8. The cam groove type engine valve mechanism according to claim 7, characterized in that: The oil deflector ring (431) is also provided with an overflow hole (432).

9. The cam groove type engine valve mechanism according to claim 4, characterized in that: The oil inlet passage (101) and / or the oil drain passage (102) are inclined inwardly from top to bottom at one end close to the cylinder seat (4).

10. An engine, characterized in that: It comprises a cam groove type engine valve mechanism as described in any one of claims 1 to 9.

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