Conjugated double-cam type engine valve mechanism and engine

Abstract

The invention belongs to the technical field of engines, and particularly relates to a conjugate double-cam 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, and the cam structure comprises a first cam disc and a second cam disc which are arranged in a conjugate mode; the air valve is axially installed on the cylinder head body in a sliding mode, two installation bases are transversely arranged on the air valve, bearings are rotatably installed on the installation bases, one bearing is attached to the outer edge of the first cam disc, and the other bearing is attached to the outer edge of the second cam disc. The cylinder head body comprises a guide cylinder; and a cylinder seat is mounted on the air valve and is mounted in the guide cylinder in a sliding manner. 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 conjugated double cam 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 conjugate double cam 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, and in serious cases, the valve mechanism parts will fly off.

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

[0008] A conjugate double cam engine valve mechanism, comprising:

[0009] Cylinder head body;

[0010] A cam structure drivingly connected to the crankshaft, the cam structure being rotatably mounted on the cylinder head body, the cam structure comprising a first cam plate and a second cam plate arranged in conjugate;

[0011] The valve is axially slidably mounted on the cylinder head body, and two mounting seats are transversely arranged on the valve. Bearings are rotatably mounted on the mounting seats, one of the bearings is in contact with the outer edge of the first cam disc, and the other bearing is in contact with the outer edge of the second cam disc.

[0012] It is further defined that the cylinder head body includes a guide cylinder;

[0013] A cylinder seat is installed on the air valve, and the cylinder seat is slidably installed in the guide cylinder.

[0014] 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.

[0015] It is further defined that a guide tube is installed on the cylinder head body, and the valve is slidably installed in the guide tube.

[0016] Such a structural design further enhances the stability of the sliding installation between the valve and the cylinder head body through the mutual cooperation of the valve and the guide tube, and is highly practical.

[0017] It is further defined that the valve is sleeved with a rod sleeve, and the mounting seat is fixedly mounted on the rod sleeve;

[0018] The rod sleeve is located below the cylinder seat, and a first elastic structure is provided between the rod sleeve and the cylinder seat;

[0019] The valve is provided with a limiting mechanism below the rod sleeve, and a second elastic structure is provided between the limiting mechanism and the rod sleeve.

[0020] Such a structural design enables the valve to have a certain degree of freedom relative to the mounting seat through the mutual cooperation between the rod sleeve and the valve, and enables the valve to have a certain degree of freedom of axial movement relative to the rod sleeve in cooperation with the first elastic structure and the second elastic structure, so that the valve can move synchronously with the rod sleeve and also has a certain degree of freedom of axial movement relative to the rod sleeve;

[0021] Thus, before the stem sleeve reaches the top dead center, the valve first contacts the valve seat. As the cam structure rotates further, the valve has a tendency to move upward synchronously under the action of the stem sleeve. This tendency is applied to the valve seat to form a seating force, thereby completing the sealing of the valve to the valve seat.

[0022] 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.

[0023] It is further defined that a cavity is formed at the lower end of the cartridge seat, and a connecting hole connected to the cavity is formed on the side wall of the cartridge seat;

[0024] The upper part of the rod sleeve is inserted into the cavity and blocks the lower end of the cavity;

[0025] The cylinder head body is also provided with an oil inlet passage and an oil drain passage connected with the guide cylinder, a one-way valve is arranged in the oil drain passage, the oil inlet passage is located below the oil drain passage, the oil inlet passage is connected with the hydraulic pump, and the oil drain passage is connected with the oil tank.

[0026] Such a structural design, through the arrangement of the oil inlet passage and the oil drain passage, cooperates with the one-way valve arranged in the oil drain passage. Before the rod sleeve moves downward from the top dead center to the connection between the oil inlet passage and the cavity, and before the rod sleeve moves upward from the bottom dead center to the connection between the oil drain passage and the cavity, based on the incompressible property of hydraulic oil, the cylinder seat, valve and rod sleeve can be regarded as a whole. That is, the hydraulic oil is utilized to make the cylinder seat, valve and rod sleeve form a rigid connection at this time, avoiding the problem of low accuracy of the opening time caused by the axial sliding freedom between the valve and the rod sleeve during the movement of the valve driven by the rod sleeve, thereby improving the control accuracy of the valve opening time.

[0027] It is further defined that there are a plurality of the communicating holes, and the plurality of communicating holes are circumferentially arranged along the central axis of the cartridge seat;

[0028] The outer wall of the cylinder seat is also provided with a first annular groove which is connected with the connecting hole.

[0029] Such a structural design, through the provision of a plurality of connecting holes, cooperates with the first annular groove, so that the hydraulic oil can enter and exit the cavity more easily, and is highly practical.

[0030] It is further defined that the inner wall of the guide cylinder is provided with a second annular groove, and the second annular groove is communicated with the oil inlet passage;

[0031] The width of the second annular groove is greater than the diameter of the connecting hole.

[0032] This structural design, through the setting of a second annular groove with a width dimension larger than the diameter dimension of the connecting hole, enables the oil inlet passage to be connected with the connecting hole within a larger stroke range of the cylinder seat, thereby increasing the time for injecting hydraulic oil into the cavity and being more practical.

[0033] It is further defined that the valve is inserted into the cartridge seat, and a first fixing structure for limiting the upward movement of the cartridge seat relative to the valve is fixedly provided above the cartridge seat;

[0034] The first fixing structure is a semicircular locking clamp with two outer walls tilted inward from top to bottom, and a conical groove is formed on the upper end surface of the cylinder seat;

[0035] The inner wall of the semicircular locking clamp is provided with a half ring, and the outer wall of the valve is provided with a first ring groove.

[0036] This structural design, through the mutual cooperation of the semicircular locking clamp, the conical groove, the half ring and the first ring groove, completes the restriction of the upward movement freedom of the cylinder seat relative to the valve. It has a simple structure, is easy to install and has strong practicality.

[0037] It is further defined that a flange ring is fixedly provided on the outer wall of the bearing close to one side of the mounting seat, and the end surfaces of the two flange rings are respectively pressed against the end surfaces of the corresponding first cam plate and the second cam plate.

[0038] This structural design limits the rotational freedom of the component with the mounting seat by abutting the first cam disc / the second cam disc with the flange ring, thereby preventing the bearing from disengaging from the first cam disc / the second cam disc during operation, and is highly practical.

[0039] An engine comprises the above-mentioned conjugated dual cam engine valve mechanism.

[0040] The invention adopting the above technical solution has the following advantages:

[0041] 1. By fitting the first cam disc and the second cam disc in the cam structure with a bearing respectively, the rotation of the cam structure is used to directly drive the valve to move axially, thereby realizing the opening and closing of the valve, without the need to configure a reset spring for driving the valve to reset, thereby avoiding the problem of movement difference of the engine at high speed caused by elastic deformation of the reset spring in the valve structure;

[0042] 2. The technical purpose of axial sliding installation of the valve on the cylinder head body is achieved through the cooperation between the guide cylinder and the cylinder seat. It has a simple structure, is easy to install, and is highly practical.

[0043] 3. Through the mutual cooperation between the stem sleeve and the valve, the valve has a certain degree of freedom relative to the mounting seat. With the cooperation of the first elastic structure and the second elastic structure, the valve can move synchronously with the stem sleeve and has a certain degree of freedom of axial movement relative to the stem sleeve.

[0044] Thus, before the stem sleeve reaches the top dead center, the valve first contacts the valve seat. As the cam structure rotates further, the valve has a tendency to move upward synchronously under the action of the stem sleeve. This tendency is applied to the valve seat to form a seating force, thereby completing the sealing of the valve to the valve seat.

[0045] Avoid the problem of insufficient valve seating force caused by the rigid contact between the valve and the cam structure, which in turn affects the sealing between the valve and the valve seat;

[0046] 4. Through the setting of the oil inlet passage and the oil drain passage, in coordination with the one-way valve set in the oil drain passage, before the rod sleeve moves downward from the top dead center to the connection between the oil inlet passage and the cavity, and before the rod sleeve moves upward from the bottom dead center to the connection between the oil drain passage and the cavity, based on the incompressible property of hydraulic oil, the cylinder seat, valve and rod sleeve can be regarded as a whole, that is, the cylinder seat, valve and rod sleeve are rigidly connected by hydraulic oil at this time, avoiding the problem of low opening time accuracy caused by the axial sliding freedom between the valve and the rod sleeve during the movement of the valve driven by the rod sleeve, thereby improving the control accuracy of the valve opening time. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The present invention can be further illustrated by the non-limiting examples given in the accompanying drawings;

[0048] Figure 1 It is a structural schematic diagram of a conjugated dual-cam engine valve train and an engine embodiment of the present invention;

[0049] Figure 2 It is a structural schematic diagram of a conjugate double cam engine valve mechanism and a cam structure, a valve, a rod sleeve and a cartridge seat part in an engine embodiment of the present invention;

[0050] Figure 3 It is a structural schematic diagram of a conjugated dual-cam engine valve mechanism and a cam structure part in an engine embodiment of the present invention;

[0051] Figure 4 It is a cross-sectional structural schematic diagram of a conjugated dual-cam engine valve mechanism and an engine embodiment of the present invention;

[0052] Figure 5 for Figure 4 A schematic diagram of the enlarged structure at A in the middle;

[0053] Figure 6 for Figure 4 A schematic diagram of the enlarged structure at B in the middle;

[0054] The main component symbols are described as follows:

[0055] Cylinder head body 1, oil inlet passage 101, oil drain passage 102, guide cylinder 11, guide tube 12, valve seat 13,

[0056] Cam structure 2, first cam disc 21, second cam disc 22,

[0057] Valve 3, rod sleeve 30, mounting seat 31, bearing 32, flange ring 320,

[0058] The cartridge seat 4, the first elastic structure 40, the first fixing structure 401,

[0059] Cavity 41, connecting hole 42, first annular groove 421, second annular groove 422,

[0060] The limiting seat 5 , the second elastic structure 50 , and the second fixing structure 501 . DETAILED DESCRIPTION

[0061] 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.

[0062] like Figures 1 to 6 As shown, a conjugate double cam engine valve mechanism of the present invention comprises:

[0063] Cylinder head body 1;

[0064] A cam structure 2 drivingly connected to the crankshaft, the cam structure 2 being rotatably mounted on the cylinder head body 1, and the cam structure 2 comprising a first cam plate 21 and a second cam plate 22 arranged in conjugate;

[0065] The valve 3 is axially slidably mounted on the cylinder head body 1, and two mounting seats 31 are horizontally arranged on the valve 3. Bearings 32 are rotatably mounted on the mounting seats 31, one of the bearings 32 is in contact with the outer edge of the first cam disc 21, and the other bearing 32 is in contact with the outer edge of the second cam disc 22.

[0066] The cylinder head body 1 includes a guide cylinder 11;

[0067] A cylinder seat 4 is mounted on the valve 3 , and the cylinder seat 4 is slidably mounted in the guide cylinder 11 .

[0068] 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.

[0069] A guide tube 12 is installed on the cylinder head body 1 , and the valve 3 is slidably installed in the guide tube 12 .

[0070] 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.

[0071] The valve 3 is sleeved with a rod sleeve 30, and the mounting seat 31 is fixedly mounted on the rod sleeve 30;

[0072] The rod sleeve 30 is located below the cylinder seat 4, and a first elastic structure 40 is provided between the rod sleeve 30 and the cylinder seat 4;

[0073] The valve 3 is provided with a limiting mechanism below the rod sleeve 30 , and a second elastic structure 50 is provided between the limiting mechanism and the rod sleeve 30 .

[0074] In fact, according to actual conditions, the mounting seat 31 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 stem sleeve 30 and the valve 3 cooperate with each other, so that the valve 3 has a certain degree of freedom relative to the mounting seat 31. With the first elastic structure 40 and the second elastic structure 50, the valve 3 can move synchronously with the stem sleeve 30, and the valve 3 also has a certain degree of freedom of axial movement relative to the stem sleeve 30.

[0075] Thus, before the rod sleeve 30 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 rod sleeve 30. 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.

[0076] 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.

[0077] A cavity 41 is formed at the lower end of the cartridge seat 4, and a connecting hole 42 communicating with the cavity 41 is formed on the side wall of the cartridge seat 4;

[0078] The upper portion of the rod sleeve 30 is inserted into the cavity 41 and blocks the lower end of the cavity 41;

[0079] The cylinder head body 1 is also provided with an oil inlet passage 101 and an oil drain passage 102 which are connected to the guide cylinder 11. A one-way valve is provided in the oil drain passage 102. The oil inlet passage 101 is located below 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.

[0080] By setting the oil inlet passage 101 and the oil drain passage 102, in cooperation with the one-way valve set in the oil drain passage 102, before the rod sleeve 30 moves downward from the top dead center to the oil inlet passage 101 connecting with the cavity 41, and before the rod sleeve 30 moves upward from the bottom dead center to the oil drain passage 102 connecting with the cavity 41, based on the incompressible property of hydraulic oil, the cartridge seat 4, the valve 3 and the rod sleeve 30 can be regarded as a whole, that is, the cartridge seat 4, the valve 3 and the rod sleeve 30 are rigidly connected by utilizing hydraulic 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 rod sleeve 30 during the movement of the valve 3 driven by the rod sleeve 30, thereby improving the control accuracy of the opening time of the valve 3.

[0081] A one-way valve is also provided in the oil inlet passage 101 .

[0082] By setting the one-way valve in the oil inlet passage 101, after the cam structure 2 drives the rod sleeve 30 to pass the bottom dead center, before the rod sleeve 30 rises again to the connecting hole 42 to disconnect from the oil inlet passage 101, the rod sleeve 30 has a tendency to move upward relative to the valve 3, that is, when the volume of the cavity 41 tends to decrease, the problem of excessive instantaneous oil pressure in the cavity 41 and the backflow of oil in the oil inlet passage 101 caused by the pressure is avoided.

[0083] There are multiple communicating holes 42, and the multiple communicating holes 42 are arranged circumferentially along the central axis of the cylinder seat 4;

[0084] The outer wall of the cartridge seat 4 is further provided with a first annular groove 421 which is in communication with the communication hole 42 .

[0085] 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 in conjunction with the first annular groove 421, so that the hydraulic oil can enter and exit the cavity 41 more easily, and the practicability is strong.

[0086] The inner wall of the guide cylinder 11 is provided with a second annular groove 422 , and the second annular groove 422 is connected to the oil inlet passage 101 ;

[0087] The width of the second annular groove 422 is greater than the diameter of the communicating hole 42 .

[0088] In fact, it can also be achieved by increasing the diameter of the connecting hole 42 according to actual conditions. In this embodiment, a second annular groove 422 having a width larger than the diameter of the connecting hole 42 is provided, so that the oil inlet channel 101 can be connected with the connecting hole 42 within a larger stroke range of the cylinder seat 4, thereby increasing the time for injecting hydraulic oil into the cavity 41 and having strong practicality.

[0089] The first elastic structure 40 is a compression spring, which is sleeved on the valve 3 and located in the cavity 41 .

[0090] In fact, according to actual conditions, an elastic structure such as a disc spring can be selected outside the cavity 41 as the first elastic structure 40. In this embodiment, a compression spring is used as the first elastic structure 40, and the rod sleeve 30 is used to apply a seating force to the valve 3. The structure is simple, and the compression spring can be placed in the cavity 41. While protecting the elastic structure, it does not occupy too much space in the cavity 41, and sufficient space is reserved for hydraulic oil, which is very practical.

[0091] The second elastic structure 50 is a disc spring.

[0092] In fact, a compression spring can also be selected as the second elastic structure 50 according to actual conditions. In this embodiment, a disc spring is used as the second elastic structure 50, which cooperates with the rod sleeve 30 and the limiting mechanism to apply restoring force to the valve 3. It has a simple structure, is easy to install, and is highly practical.

[0093] The valve 3 is inserted into the cartridge seat 4, and a first fixing structure 401 is fixed above the cartridge seat 4 for limiting the upward movement of the cartridge seat 4 relative to the valve 3;

[0094] The first fixing structure 401 is a semicircular locking clamp with two outer walls tilted inward from top to bottom, and a conical groove is formed on the upper end surface of the cylinder seat 4;

[0095] 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 first ring groove.

[0096] In fact, according to actual conditions, the connection between the cartridge seat 4 and the valve 3 can be achieved by directly screwing the cartridge seat 4 onto the valve 3. This embodiment restricts the upward movement freedom of the cartridge seat 4 relative to the valve 3 through the cooperation of the semicircular locking clamp, the conical groove, the half ring and the first ring groove. It has a simple structure, is easy to install and is highly practical.

[0097] The limiting mechanism comprises a limiting seat 5 sleeved on the valve 3 and a second fixing structure 501;

[0098] The lower end surface of the limiting seat 5 is provided with a conical groove;

[0099] The second fixing structure 501 is a semicircular locking clamp with two outer walls inclined outward from top to bottom;

[0100] 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.

[0101] 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 freedom of downward movement of the limit mechanism relative to the valve 3. This embodiment restricts the freedom of downward movement 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 rod sleeve 30. It has a simple structure, is easy to install, and is highly practical.

[0102] A flange ring 320 is fixedly provided on the outer wall of the bearing 32 near the mounting seat 31 , and the end surfaces of the two flange rings 320 are respectively pressed against the end surfaces of the corresponding first cam disc 21 and the second cam disc 22 .

[0103] By using the flange ring 320 to press against the first cam disc 21 / the second cam disc 22, the rotational freedom of the component provided with the mounting seat 31 is restricted, so as to prevent the bearing 32 from being separated from the contact with the first cam disc 21 / the second cam disc 22 during operation, which is highly practical.

[0104] An engine comprises the above-mentioned conjugated dual cam engine valve mechanism.

[0105] In this embodiment, when in use, the cam structure 2 rotates along with the crankshaft, driving the first cam plate 21 and the second cam plate 22 to rotate;

[0106] When the two bearings 32 are respectively against the edge of the first cam disc 21 farther from the rotation center of the cam structure 2 and the edge of the second cam disc 22 closer to the rotation center of the cam structure 2, that is, when the rod sleeve 30 is at the top dead center, the valve 3 is against the valve seat 13, and the valve 3 is in a closed state. At this time, the communicating hole 42 is connected with the oil drain passage 102 through the first annular groove 421, and the first elastic structure 40 forms an upward thrust on the cylinder seat 4, which then overcomes the prestress of the second elastic structure 50 through the valve 3, forming a seating force of the valve 3 on the valve seat 13, completing the sealing between the valve 3 and the valve seat 13, as shown in FIG. Figure 1 and Figure 4-Figure 6 As shown;

[0107] The cam structure 2 continues to rotate until the two bearings 32 are separated from the edge of the first cam plate 21 farther from the rotation center of the cam structure 2 and the edge of the second cam plate 22 closer to the rotation center of the cam structure 2, respectively, and then start to drive the rod sleeve 30 to move downward relative to the cylinder head body 1 until the communication hole 42 is separated from the communication with the oil drain passage 102;

[0108] During this process, the rod sleeve 30 has a tendency to move downward relative to the valve 3, that is, the volume of the cavity 41 tends to increase. Since a one-way valve is provided in the oil drain channel 102, the hydraulic oil is prevented from entering the cavity 41 through the oil drain channel 102. Based on the incompressible property of the hydraulic oil, at this time, the cartridge seat 4, the valve 3 and the rod sleeve 30 can be regarded as a whole, that is, the cartridge seat 4, the valve 3 and the rod sleeve 30 are rigidly connected by the hydraulic oil. During this process, the valve 3 moves downward synchronously with the rod sleeve 30, thereby accurately completing the opening of the valve 3.

[0109] The cam structure 2 continues to rotate, and the rod sleeve 30 continues to move downward. After the connecting hole 42 is disconnected from the oil drain passage 102, until the connecting hole 42 is connected to the oil inlet passage 101, the cavity 41 is in a closed state. At this time, based on the incompressible property of the hydraulic oil, the cylinder seat 4, the valve 3 and the rod sleeve 30 can be regarded as a whole, that is, the cylinder seat 4, the valve 3 and the rod sleeve 30 are rigidly connected by the hydraulic oil. In this process, the valve 3 moves downward synchronously with the rod sleeve 30, thereby further increasing the opening degree of the valve 3.

[0110] The cam structure 2 continues to rotate, and the rod sleeve 30 continues to move downward until the connecting hole 42 is connected to the oil inlet passage 101, and the rigid connection is broken. The hydraulic pump injects hydraulic oil into the cavity 41 through the oil inlet passage 101, so that the pressure in the cavity 41 increases, overcoming the prestress of the second elastic structure 50, so that the valve 3 moves downward relative to the cylinder head body 1 under the drive of the rod sleeve 30, and the valve 3 moves upward relative to the rod sleeve 30 until the cam structure 2 drives the rod sleeve 30 to pass the bottom dead center;

[0111] In this process, the upward movement of the valve 3 relative to the rod sleeve 30 is used to prepare a displacement for the upward movement of the rod sleeve 30 relative to the valve 3 after the valve is seated next time;

[0112] The cam structure 2 continues to rotate. After the cam structure 2 drives the rod sleeve 30 to pass the lower dead center, before the rod sleeve 30 rises again to the connecting hole 42 to disconnect from the oil inlet passage 101, the rod sleeve 30 has a tendency to move upward relative to the valve 3, that is, the volume of the cavity 41 tends to decrease. Since 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 41, and a one-way valve is provided in the oil inlet passage 101 to prevent the hydraulic oil from entering the oil inlet passage 101 through the cavity 41. Based on the incompressible property of the hydraulic oil, at this time, the cartridge seat 4, the valve 3 and the rod sleeve 30 can be regarded as a whole, that is, the cartridge seat 4, the valve 3 and the rod sleeve 30 are rigidly connected by the hydraulic oil. In this process, the valve 3 moves upward synchronously with the rod sleeve 30, thereby accurately completing the control of the valve 3.

[0113] The cam structure 2 continues to rotate. After the connecting hole 42 is disconnected from the oil inlet passage 101, before the connecting hole 42 is connected to the oil drain passage 102 again, the cavity 41 is in a closed state. Based on the incompressible property of the hydraulic oil, the cylinder seat 4, the valve 3 and the rod sleeve 30 can be regarded as a whole, so that the valve 3 moves upward synchronously with the rod sleeve 30.

[0114] Until the valve 3 contacts the valve seat 13 again, at this time, the communicating hole 42 is reconnected with the oil drain passage 102 via the first annular groove 421, and the hydraulic oil in the cavity 41 starts to leak from the oil drain passage 102 via the one-way valve, the rigid connection state is destroyed, and the cam structure 2 continues to rotate until the rod sleeve 30 reaches the top dead center;

[0115] During the process from the time when the valve 3 begins to contact with the valve seat 13 to the time when the rod sleeve 30 reaches the top dead center, the rod sleeve 30 continues to move upward relative to the cylinder head body 1 under the action of the cam structure 2, and due to the contact between the valve 3 and the valve seat 13, the valve 3 cannot move, and an upward thrust is formed on the cylinder seat 4 through the first elastic structure 40, and then through the valve 3, a seating force of the valve 3 on the valve seat 13 is formed, thereby completing the sealing between the valve 3 and the valve seat 13.

[0116] The above is a detailed introduction to a conjugate double cam 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 conjugate double cam engine valve train, 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 first cam plate (21) and a second cam plate (22) which are arranged in conjugate relation; A valve (3), the valve (3) being axially slidably mounted on the cylinder head body (1), the valve (3) being laterally provided with two mounting seats (31), the mounting seats (31) being rotatably mounted with bearings (32), one of the bearings (32) being in contact with the outer edge of the first cam disc (21), and the other of the bearings (32) being in contact with the outer edge of the second cam disc (22).

2. A conjugated dual cam engine valve train according to claim 1, characterized in that: The cylinder head body (1) comprises 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 conjugate double cam engine valve train according to claim 1, characterized in that: A guide tube (12) is installed on the cylinder head body (1), and the valve (3) is slidably installed in the guide tube (12).

4. A conjugated dual cam engine valve train according to claim 2, characterized in that: The valve (3) is sleeved with a rod sleeve (30), and the mounting seat (31) is fixedly mounted on the rod sleeve (30); The rod sleeve (30) is located below the cylinder seat (4), and a first elastic structure (40) is provided between the rod sleeve (30) and the cylinder seat (4); The valve (3) is provided with a limiting mechanism below the rod sleeve (30), and a second elastic structure (50) is provided between the limiting mechanism and the rod sleeve (30).

5. A conjugated dual cam engine valve train according to claim 4, characterized in that: A cavity (41) is formed at the lower end of the cartridge seat (4), and a communication hole (42) communicating with the cavity (41) is formed on the side wall of the cartridge seat (4); The upper portion of the rod sleeve (30) is inserted into the cavity (41) and forms a seal on the lower end of the cavity (41); The cylinder head body (1) is also provided with an oil inlet passage (101) and an oil drain passage (102) which are in communication with the guide cylinder (11); a one-way valve is provided in the oil drain passage (102); the oil inlet passage (101) is located below 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.

6. A conjugated dual cam engine valve train according to claim 5, characterized in that: There are a plurality of communicating holes (42), and the plurality of communicating holes (42) are arranged circumferentially along the central axis of the cartridge seat (4); The outer wall of the cartridge seat (4) is also provided with a first annular groove (421) which is in communication with the communication hole (42).

7. A conjugate double cam engine valve train according to claim 5, characterized in that: A second annular groove (422) is formed on the inner wall of the guide cylinder (11), and the second annular groove (422) is communicated with the oil inlet passage (101); The width of the second annular groove (422) is greater than the diameter of the connecting hole (42).

8. A conjugate double cam engine valve train according to claim 4, characterized in that: The air valve (3) is inserted into the cartridge seat (4), and a first fixing structure (401) is fixedly provided above the cartridge seat (4) for limiting the upward movement of the cartridge seat (4) relative to the air valve (3); The first fixing structure (401) is a semicircular locking clamp with two outer walls inclined inward from top to bottom, and the upper end surface of the cartridge seat (4) is provided with a conical groove; 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 first ring groove.

9. A conjugate double cam engine valve train according to claim 1, characterized in that: A flange ring (320) is fixedly provided on the outer wall of the bearing (32) at one side close to the mounting seat (31), and the end surfaces of the two flange rings (320) respectively abut against the end surfaces of the corresponding first cam disc (21) and second cam disc (22).

10. An engine, characterized in that: It comprises a conjugated dual cam engine valve mechanism as described in any one of claims 1-9.

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