Hydraulically driven rotating actuator, fully variable hydraulic valve system and control method

Abstract

The application provides a hydraulic drive rotating driver, a full-variable hydraulic valve system and a control method, and belongs to the technical field of hydraulic drive and comprises a driver shell, a driver rotor and an electromagnetic valve; the driver shell and the driver rotor form a hydraulic cavity; the driver shell is provided with the driver rotor and the electromagnetic valve; each blade of the driver rotor divides the hydraulic cavity formed by the driver shell and the driver rotor into two parts, i.e., a left part and a right part; the hydraulic cavity formed on the left side of the blade is defined as an A cavity, and the hydraulic cavity formed on the right side of the blade is defined as a B cavity; the electromagnetic valve controls the inflow and outflow of hydraulic oil in different channels, a pressure difference is established between the A cavity and the B cavity of the rotor blade, and the driver rotor is driven to rotate.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic drive technology, and particularly relates to a hydraulically driven drive, a fully variable hydraulic valve system, and a control method. Background Technology

[0002] The statements in this section are merely background information related to the present invention and do not necessarily constitute prior art.

[0003] To further optimize internal combustion engine technologies, researchers have developed a fully variable hydraulic valve system that allows for continuous variation in valve timing, valve opening duration, and maximum valve lift. However, existing systems suffer from high operating costs, overly complex system components, and poor response performance.

[0004] The control of valve movement in a fully variable hydraulic valve system is achieved by controlling the connection and disconnection of the high-pressure and low-pressure oil chambers in the hydraulic system. The oil discharge phase of the control valve between the high-pressure and low-pressure oil chambers is mostly controlled by an electric motor. However, due to the limitations of its own mechanical and physical characteristics, if it is applied to an internal combustion engine, higher requirements are placed on the overall oil discharge mechanism.

[0005] Chinese invention patent ZL201310296611.0 discloses an oil control device for a fully variable hydraulic valve system of an internal combustion engine. The device is connected to the hydraulically driven valve system of the internal combustion engine and consists of a housing and a rotary valve, a hydraulic accumulator and a transmission mechanism installed in the housing. It is an oil control device for a fully variable hydraulic valve system that can replace high-frequency solenoid valves in single-cylinder and multi-cylinder internal combustion engines.

[0006] In terms of control method, the device drives the rack that meshes with the gear of the rotary valve sleeve through a servo motor, thereby driving the rotary valve sleeve to rotate and changing the circumferential position of the radial oil hole on the rotary valve sleeve, thus changing the oil discharge time. However, the servo motor is too large, expensive, and can only withstand temperatures of 80°C, which makes it difficult to apply in actual control. Summary of the Invention

[0007] To overcome the shortcomings of the prior art, the present invention provides a hydraulically driven actuator, a fully variable hydraulic valve system, and a control method. The oil discharge time of the fully variable hydraulic valve system can be changed by the rotation of the rotor, so as to achieve the purpose of continuously variable valve timing, valve opening duration, and maximum valve lift, thereby greatly improving the power and economy of the internal combustion engine.

[0008] To achieve the above objectives, one or more embodiments of the present invention provide the following technical solutions:

[0009] In the first aspect, a hydraulically driven actuator is disclosed, comprising:

[0010] Driver housing, driver rotor, and solenoid valve;

[0011] The driver housing and the driver rotor form a hydraulic chamber; the driver rotor and a solenoid valve are mounted on the driver housing;

[0012] Each blade of the driver rotor divides the hydraulic cavity formed by the driver housing and the driver rotor into two parts, left and right. The hydraulic cavity formed on the left side of the blade is defined as cavity A, and the hydraulic cavity formed on the right side of the blade is defined as cavity B.

[0013] By controlling the inflow and outflow of hydraulic oil in different channels using solenoid valves, a pressure difference is established between the A and B chambers of the rotor blades, thereby driving the drive rotor to rotate.

[0014] As a further technical solution, the driver housing is provided with multiple hydraulic oil channels, axial oil holes C and multiple hydraulic oil ports;

[0015] The driver rotor is provided with a central hydraulic oil channel, a sixth hydraulic oil channel, a seventh hydraulic oil channel and an eighth hydraulic oil channel.

[0016] The solenoid valve is equipped with an oil inlet channel.

[0017] As a further technical solution, each of the A chambers is connected to a corresponding hydraulic oil passage on the driver rotor, the hydraulic oil passage is connected to the central hydraulic oil passage, and a hydraulic oil port is opened on the central hydraulic oil passage.

[0018] The hydraulic port is connected to the second hydraulic oil passage of the driver housing. The second hydraulic oil passage is connected to the first hydraulic oil passage through the axial oil hole C. The first hydraulic oil passage receives hydraulic oil from the solenoid valve inlet through the solenoid valve inlet passage.

[0019] As a further technical solution, each of the B chambers is connected to a corresponding hydraulic port on the actuator housing, and the hydraulic port is connected to a corresponding hydraulic oil passage. The fourth hydraulic oil passage receives hydraulic oil from the inlet of the solenoid valve through the inlet passage of the solenoid valve.

[0020] As a further technical solution, the drive rotor and the drive housing are sealed with a sealing plate. A sealing groove is opened at the top of each blade of the drive rotor, and a top sealing plate is installed in the sealing groove. The top sealing plate is composed of a top sealing plate spring, a top sealing plate and a side plate, which maintains the sealing of hydraulic oil and cleans the friction surface of the drive housing by the elastic force of the top sealing plate spring.

[0021] As a further technical solution, it also includes a driver end cover, which is sealed to the end of the driver rotor by an O-ring. An annular groove is opened on the circumferential surface of the end of the driver rotor, and an O-ring is installed in the annular groove. The O-ring is in close contact with the driver end cover to maintain the sealing of the hydraulic oil.

[0022] As a further technical solution, an angle sensor is also included. The angle sensor and the driver end cover are sealed with an O-ring. An annular sealing groove is opened on the top surface of the driver end cover to maintain the seal between the angle sensor and the driver end cover.

[0023] As a further technical solution, the oil inlet channel at the oil inlet of the drive housing is sealed with an O-ring between it and the hydraulic oil source. The oil inlet channel has an annular sealing groove, and an O-ring is installed in the annular sealing groove to maintain the sealing of the hydraulic oil.

[0024] As a further technical solution, the driver end cover has a radial drain hole, which is directly connected to the external environment, and excess hydraulic oil flows directly into the outside through the radial drain hole.

[0025] Secondly, a fully variable hydraulic valve system is disclosed, including:

[0026] A hydraulically driven actuator, and a control valve;

[0027] The hydraulically driven actuator includes at least an actuator rotor, and the oil control valve includes a rotary valve core and a rotary valve sleeve.

[0028] The driver rotor meshes with the gear on the rotary valve sleeve of the oil control valve through the gear sector, driving the rotary valve sleeve to rotate, and the rotary valve core of the oil control valve rotates synchronously with the camshaft.

[0029] Both the rotary valve core and the rotary valve sleeve are provided with matching oil drain holes. By changing the relative positions of the oil drain holes of the rotary valve core and the rotary valve sleeve, oil draining can be achieved at different phase times, thus realizing full variability.

[0030] Thirdly, a control method for a fully variable hydraulic valve system is disclosed, including:

[0031] The rotation of the valve cam causes the rotary valve core of the oil control valve to rotate synchronously;

[0032] When the radial oil hole of the rotary valve core rotates to the point where it is no longer connected to the radial oil hole of the rotary valve sleeve, the control valve is in the closed state, the valve cam drives the hydraulic tappet in the hydraulic chamber, and the oil overcomes the elastic force of the valve spring to drive the valve to open.

[0033] When the radial oil hole of the rotary valve core rotates to coincide with the radial oil hole of the rotary valve sleeve, the oil control valve is in the open state, the system begins to drain oil, and the valve closes.

[0034] When it is necessary to change the system's oil drain phase, the solenoid valve is controlled to drive the actuator rotor to rotate. The gear sector on the actuator rotor rotates synchronously with the actuator rotor, driving the gear on the rotary valve sleeve of the control valve to rotate, thereby driving the rotary valve sleeve of the control valve to rotate. The circumferential position of the radial oil hole of the rotary valve sleeve also changes accordingly, thus changing the oil drain phase of the control valve, achieving the purpose of controlling valve timing, valve opening duration, and valve lift to be fully variable.

[0035] As a further technical solution, the hydraulic oil used during oil draining comes from the internal combustion engine's own lubrication system.

[0036] The above one or more technical solutions have the following beneficial effects:

[0037] The technical solution of this invention controls the inflow and outflow of hydraulic oil in different channels by controlling a solenoid valve, establishing a pressure difference on both sides of the rotor blades of the swing cylinder, thereby driving the rotor to rotate and achieving the purpose of hydraulically driven rotation. When used in conjunction with the FHVVS, this rotating device can change the oil release time of the fully variable hydraulic valve system through the rotation of the rotor, achieving continuously variable valve timing, valve opening duration, and maximum valve lift, thus greatly improving the power and economy of the internal combustion engine.

[0038] The technical solution of this invention can replace the servo motor as the oil drain drive device in a fully variable hydraulic valve system. It has a compact structure and better temperature resistance. The overall sealing effect of this invention is good, employing sealing methods such as top sealing plates to reduce hydraulic oil leakage. The hydraulically driven actuator of this invention has good scalability and great application potential, and can be used as a hydraulically driven rotating device in related technical fields.

[0039] Advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0040] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0041] Figure 1 This is a schematic cross-sectional view of the overall structure of an embodiment of the present invention;

[0042] Figure 2 This is a schematic cross-sectional view of the sub-driver housing according to an embodiment of the present invention;

[0043] Figure 3 This is an embodiment of the present invention. Figure 2 BB cross-section;

[0044] Figure 4 This is an embodiment of the present invention. Figure 2 CC cross-section;

[0045] Figure 5 This is a schematic cross-sectional view of the sub-driver rotor according to an embodiment of the present invention;

[0046] Figure 6 This is an embodiment of the present invention. Figure 5 AA cross-section view;

[0047] Figure 7 This is a schematic cross-sectional view of the sub-driver end cap according to an embodiment of the present invention.

[0048] In the diagram, 1. Angle sensor, 2. First O-ring seal, 3. Driver end cover, 4. Second O-ring seal, 5. Driver rotor, 6. Driver housing, 7. Needle roller bearing, 8. Third O-ring seal, 9. Solenoid valve, 10. First hydraulic oil passage, 11. Axial oil hole C, 12. Second hydraulic oil passage, 13. First hydraulic oil port, 14. Third hydraulic oil passage, 15. Second hydraulic oil port, 16. Fourth hydraulic oil passage, 17. Third hydraulic oil port, 18. Fifth hydraulic oil passage, 19. Oil inlet, 20. Oil return port, 21. Fourth hydraulic oil port, 22. Central hydraulic oil passage, 23. Sixth hydraulic oil passage, 24. Seventh hydraulic oil passage, 25. Eighth hydraulic oil passage, 26. Radial drain hole. Detailed Implementation

[0049] It should be noted that the following detailed descriptions are exemplary and intended to provide further illustration of the invention. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains.

[0050] It should be noted that the terminology used herein is for the purpose of describing particular implementations only and is not intended to limit the exemplary implementations of the present invention.

[0051] Where there is no conflict, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0052] Terminology Explanation:

[0053] Needle roller bearings are roller bearings with cylindrical rollers that are both thin and long relative to their diameter. These rollers are called needle rollers. Despite their small cross-section, these bearings still have a high load-carrying capacity. Needle roller bearings are equipped with thin and long rollers (roller diameter D≤5mm, L / D≥2.5, where L is the roller length), resulting in a compact radial structure. With the same inner diameter and load capacity as other types of bearings, they have the smallest outer diameter, making them particularly suitable for support structures where radial installation dimensions are limited.

[0054] Example 1

[0055] This embodiment discloses a hydraulically driven actuator, including an actuator housing 6, an actuator end cover 3, an actuator rotor 5, an angle sensor 1, and a solenoid valve 9.

[0056] It should be noted that this hydraulically driven actuator can be applied to hydraulic engines.

[0057] See appendix Figure 2 As shown, the driver housing 6 consists of a rotor mounting hole, a solenoid valve mounting hole, an oil inlet 19, a first hydraulic oil channel 10, an axial oil hole C11, a second hydraulic oil channel 12, a second hydraulic oil port 15, a third hydraulic oil port 17, a first hydraulic oil port 13, a fourth hydraulic oil channel 16, a fifth hydraulic oil channel 18, a third hydraulic oil channel 14, an oil return port 20, and a needle roller bearing 7, which is located on the driver rotor 5.

[0058] The driver end cover 3 consists of screw holes, rotor mounting holes, an annular sealing groove, and radial oil drain holes 26. Figure 7 This is a schematic cross-sectional view of the driver end cover structure. The screw hole is the leftmost through hole. The rotor mounting hole is the middle through hole. The annular sealing groove is the location for installing the first O-ring 2, i.e. Figure 7 The lowest and largest circumference at the center. Radial drain hole. Figure 7 It has been marked.

[0059] The driver rotor 5 consists of a fourth hydraulic port 21, a central hydraulic oil channel 22, a sixth hydraulic oil channel 23, a seventh hydraulic oil channel 24, an eighth hydraulic oil channel 25, a first sealing groove, and a third sealing groove, etc. (See appendix) Figure 5 , Figure 6 As shown.

[0060] Solenoid valve 9 includes an oil inlet channel and an oil return channel, wherein the oil inlet channel and the oil return channel of solenoid valve 9 are connected to... Figure 2 The oil inlet 19 and oil return 20 of the drive housing 6 are connected. The position of the internal channel of the solenoid valve can be changed. The specific channel position relationship of the solenoid valve will not be described in detail.

[0061] The driver rotor 5 includes three blades. Each blade divides the hydraulic chamber formed by the driver housing 6 and the driver rotor 5 into two parts, left and right. The hydraulic chamber formed on the left side of the blade is defined as chamber A, and the hydraulic chamber formed on the right side of the blade is defined as chamber B.

[0062] Each chamber A is connected to the corresponding sixth hydraulic oil passage 23, seventh hydraulic oil passage 24 and eighth hydraulic oil passage 25 on the driver rotor 5. The sixth hydraulic oil passage 23, seventh hydraulic oil passage 24 and eighth hydraulic oil passage 25 are connected to the central hydraulic oil passage 22. The central hydraulic oil passage 22 has a fourth hydraulic oil port 21, which is connected to the second hydraulic oil passage 12 of the driver housing 6. The second hydraulic oil passage 12 is connected to the first hydraulic oil passage 10 through the axial oil hole C11. The first hydraulic oil passage 10 receives hydraulic oil from the oil inlet 19 of the solenoid valve 9 through the oil inlet passage of the solenoid valve 9. The pressure of the hydraulic chamber can be controlled more flexibly in the above manner.

[0063] Each B chamber communicates with the corresponding second hydraulic port 15, third hydraulic port 17 and first hydraulic port 13 on the actuator housing 6. The second hydraulic port 15, third hydraulic port 17 and first hydraulic port 13 communicate with the corresponding fourth hydraulic oil passage 16, fifth hydraulic oil passage 18 and third hydraulic oil passage 14. The fourth hydraulic oil passage 16 receives hydraulic oil from the oil inlet 19 of the solenoid valve 9 through the oil inlet passage of the solenoid valve 9.

[0064] Although the hydraulic oil for chambers A and B ultimately comes from the inlet 19 of solenoid valve 9, their channels flow through the driver rotor 5 and driver housing 6 respectively, allowing for separate control and preventing mutual interference, thus providing better controllability and flexibility.

[0065] To achieve overall equipment sealing, a sealing plate is used to seal the drive rotor 5 and the drive housing 6. A first sealing groove, a second sealing groove, and a third sealing groove are opened at the tip of each blade of the drive rotor 5. Each of the above sealing grooves is equipped with a top sealing plate. The top sealing plate is made of cast iron and is treated with electron beam to improve the wear resistance of the friction surface. The top sealing plate consists of a top sealing plate spring, a top sealing plate, and a side plate. It maintains the sealing of the hydraulic oil and cleans the friction surface of the drive housing 6 by the elastic force of the top sealing plate spring.

[0066] The drive end cover 3 and the end of the drive rotor 5 are sealed with a first O-ring 2. Specifically, an annular sealing groove is opened on the circumferential surface of the end of the drive rotor 5, and the first O-ring 2 is installed in the annular sealing groove. The first O-ring 2 is tightly attached to the drive end cover 3 to maintain the sealing of the hydraulic oil.

[0067] An angle sensor 1 and the driver end cover 3 are sealed with a second O-ring 4. The top surface of the driver end cover 3 has an annular sealing groove, and the second O-ring 4 is installed in the annular sealing groove to maintain the seal between the angle sensor 1 and the driver end cover 3, thus ensuring the accuracy of the angle sensor.

[0068] The oil inlet 19 of the drive housing 6 is sealed with a third O-ring 8 between the oil inlet channel and the hydraulic oil source. The oil inlet channel has an annular sealing groove, and the third O-ring 8 is installed in the annular sealing groove to maintain the sealing of the hydraulic oil and ensure sufficient hydraulic oil supply.

[0069] The driver end cover 3 has a radial drain hole 26, which is directly connected to the external environment. Excess hydraulic oil flows directly into the outside world, such as the oil pan, through the radial drain hole 26.

[0070] The working process of this invention is described below:

[0071] When the hydraulically driven drive of the present invention drives the rotor blades to rotate clockwise, hydraulic oil is pumped out from the hydraulic oil source and flows through the oil inlet 19. The oil inlet 19 is connected to the oil inlet channel A by controlling the solenoid valve 9, and at the same time the oil inlet channel B is connected to the oil drain port of the solenoid valve. The oil inlet channel A is connected to the first hydraulic oil channel 10. Hydraulic oil flows through the first hydraulic oil channel 10, axial oil hole C11, second hydraulic oil channel 12, and fourth hydraulic oil port 21 into the central hydraulic oil channel 22. It then enters the corresponding hydraulic chamber A on the left side of the three blades of the driver rotor 5 through the sixth hydraulic oil channel 23, the seventh hydraulic oil channel 24, and the eighth hydraulic oil channel 25, respectively, to establish oil pressure and drive the rotor blades to rotate clockwise. At the same time, the hydraulic oil in the B hydraulic chamber flows through the second hydraulic oil port 15, the third hydraulic oil port 17, and the first hydraulic oil port 13 to the fourth hydraulic oil channel 16, the fifth hydraulic oil channel 18, and the third hydraulic oil channel 14, and then flows through the fourth hydraulic oil channel 16 to the oil inlet 19. Since the oil inlet 19 is the same as the solenoid valve drain port at this time, the hydraulic oil in the B chamber is quickly released, and the rotor blades rotate clockwise quickly. This method can achieve a rapid response to the working conditions and has better responsiveness.

[0072] In this embodiment, when the hydraulically driven rotor blades rotate counterclockwise, hydraulic oil is pumped out from the hydraulic oil source and flows through the oil inlet 19. The oil inlet 19 is connected to the oil inlet channel B by controlling the solenoid valve, and at the same time, the oil inlet channel A is connected to the oil drain hole of the solenoid valve. The oil inlet B is connected to the fourth hydraulic oil channel 16. Hydraulic oil flows through the fourth hydraulic oil channel 16, the fifth hydraulic oil channel 18, and the third hydraulic oil channel 14, and enters the corresponding Class B hydraulic chambers on the right side of the three blades of the driver rotor 5 through the second hydraulic oil port 15, the third hydraulic oil port 17, and the first hydraulic oil port 13, respectively, to establish oil pressure and drive the rotor to rotate counterclockwise. At this time, the hydraulic oil in the A chamber flows through the sixth hydraulic oil channel 23, the seventh hydraulic oil channel 24, and the eighth hydraulic oil channel 25 to the second hydraulic oil channel 12, and then to the first hydraulic oil channel 10. The first hydraulic oil channel 10 is connected to the oil inlet 19. Since the oil inlet 19 is the same as the solenoid valve drain port at this time, the hydraulic oil in the A chamber is quickly discharged, and the rotor blades rotate counterclockwise quickly, which can achieve a rapid response to the working condition requirements and better responsiveness.

[0073] In this embodiment, the hydraulic oil pressure in chambers A and B is further balanced by controlling the solenoid valve, so that the rotor blades can maintain their position.

[0074] Example 2

[0075] The purpose of this embodiment is to provide a fully variable hydraulic valve system, including:

[0076] Actuators and control valves for hydraulically driven rotation;

[0077] The hydraulically driven actuator includes at least an actuator rotor 5, and the oil control valve includes a rotary valve core and a rotary valve sleeve;

[0078] The driver rotor 5 meshes with the gear on the rotary valve sleeve of the oil control valve through the gear sector, driving the rotary valve sleeve to rotate, and the rotary valve core of the oil control valve rotates synchronously with the camshaft.

[0079] Both the rotary valve core and the rotary valve sleeve are provided with matching drain holes. By changing the relative positions of the drain holes of the rotary valve core and the drain holes of the rotary valve sleeve, oil can be drained at different phase times, thus achieving full variability.

[0080] In this embodiment, the hydraulically driven drive includes not only the drive rotor 5, but also the aforementioned housing, end cover, solenoid valve, etc.

[0081] In application, the hydraulically driven actuator of the embodiment of the present invention can be used as a drain angle control device for a fully variable hydraulic valve system. The actuator rotor meshes with the gear on the rotary valve sleeve of the control valve in the fully variable hydraulic valve system through a gear sector, driving the rotary valve sleeve to rotate. The rotary valve core of the control valve rotates synchronously with the camshaft. Both the valve core and the valve sleeve are provided with matching drain holes. By changing the relative positions of the drain holes of the valve core and the valve sleeve, draining is achieved at different phase times, thus realizing full variable operation. Specifically, when the drain holes of the valve core and the valve sleeve do not coincide, no oil is drained; when the valve core rotates to coincide with the drain hole of the valve sleeve, oil is drained.

[0082] In this embodiment, when the hydraulically driven actuator is working, it drives the actuator rotor to rotate by controlling the switch of the solenoid valve. The gear sector on the actuator rotor rotates synchronously with the actuator rotor. The gear of the control valve sleeve meshes with the gear sector on the actuator, thereby rotating the control valve sleeve. The valve core rotates synchronously with the camshaft, and the relative position of the two changes.

[0083] Example 3

[0084] The purpose of this embodiment is to provide a control method for a fully variable hydraulic valve system, including:

[0085] When the fully variable hydraulic valve system is working, the rotation of the valve train cam drives the rotary valve core of the control valve to rotate synchronously. When the radial oil hole of the rotary valve core rotates to the point where it is no longer connected to the radial oil hole of the rotary valve sleeve, the control valve is in the closed state. The valve train cam drives the hydraulic pusher to build up high pressure in the hydraulic chamber. The high-pressure oil overcomes the elastic force of the valve spring and drives the valve to open. When the radial oil hole of the rotary valve core rotates to coincide with the radial oil hole of the rotary valve sleeve, the control valve is in the open state, the system begins to drain oil, and the valve closes.

[0086] When it is necessary to change the system's oil drain phase, the hydraulically driven actuator of this invention is in working condition. By controlling the switch of the solenoid valve, the actuator rotor is driven to rotate. The gear sector on the actuator rotor rotates synchronously with the actuator rotor, driving the gear on the rotary valve sleeve of the control valve to rotate, thereby driving the rotary valve sleeve of the control valve to rotate. The circumferential position of the radial oil hole of the rotary valve sleeve also changes accordingly, thereby changing the oil drain phase of the control valve, achieving the purpose of controlling valve timing, valve opening duration and valve lift to be fully variable.

[0087] Therefore, under the influence of this invention, different oil discharge times can be controlled according to different internal combustion engine operating conditions, thereby achieving flexible control of the valve movement law of the internal combustion engine.

[0088] The oil drain control device of this embodiment, namely the hydraulically driven actuator, plays a role in controlling the oil drain pattern between the hydraulic drive device and the low-pressure system of the fully variable hydraulic valve system. Its oil drain pattern can be flexibly controlled within a certain range. In addition, this invention can also play a sealing role, with good sealing effect, reducing the amount of hydraulic oil leakage, greatly improving the control accuracy of valve movement pattern, and has a wide range of applications, which can meet the requirements of various operating conditions of internal combustion engines.

[0089] In this embodiment, when the actuator is used as a drain actuator for a fully variable hydraulic valve system, the hydraulic oil used comes from the internal combustion engine's own lubrication system.

[0090] While the specific embodiments of the present invention have been described above in conjunction with the accompanying drawings, this is not intended to limit the scope of protection of the present invention. Those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art without creative effort based on the technical solutions of the present invention are still within the scope of protection of the present invention.

Claims

1. A fully variable hydraulic valve system, characterized by, The utility model relates to a hydraulic drive rotary driver, oil control valve, the hydraulic drive rotary driver includes driver housing, driver rotor and solenoid valve, the oil control valve includes rotary valve core and rotary valve sleeve, the driver housing and driver rotor form hydraulic cavity, the driver housing is equipped with driver rotor and solenoid valve, the driver rotor is equipped with the blade, and each blade of driver rotor divides the hydraulic cavity formed by driver housing and driver rotor into left and right two parts, defines the hydraulic cavity formed by blade left side as A cavity, and the hydraulic cavity formed by blade right side is B cavity, the solenoid valve includes oil inlet channel and oil return channel, wherein the oil inlet channel and oil return channel of solenoid valve are communicated with the oil inlet and oil return of driver housing, and the channel position in the solenoid valve can be changed, the flow in and out of hydraulic oil in different channels is controlled based on solenoid valve, and the pressure difference is established between the A cavity and B cavity of rotor blade, thereby drive driver rotor rotates, the driver housing is equipped with first hydraulic oil channel, second hydraulic oil channel, third hydraulic oil channel, fourth hydraulic oil channel, fifth hydraulic oil channel, axial oil hole C and first hydraulic oil port, second hydraulic oil port, third hydraulic oil port, the driver rotor is equipped with center hydraulic oil channel, sixth hydraulic oil channel, seventh hydraulic oil channel and eighth hydraulic oil channel, the solenoid valve is equipped with oil inlet channel, each A cavity is communicated with the corresponding hydraulic oil channel on the driver rotor, the hydraulic oil channel is communicated with the center hydraulic oil channel, and the fourth hydraulic oil port is opened on the center hydraulic oil channel, the fourth hydraulic oil port is communicated with the second hydraulic oil channel of driver housing, the second hydraulic oil channel is communicated with the first hydraulic oil channel through the axial oil hole C, and the first hydraulic oil channel receives the hydraulic oil from the oil inlet port of solenoid valve through the oil inlet channel of solenoid valve, each B cavity is communicated with the corresponding hydraulic oil port on the driver housing, and the corresponding hydraulic oil port is communicated with the corresponding hydraulic oil channel, and the fourth hydraulic oil channel receives the hydraulic oil from the oil inlet port of solenoid valve through the oil inlet channel of solenoid valve, wherein the oil channel of the hydraulic oil of A cavity is connected with the oil inlet port of solenoid valve through driver rotor, the oil channel of the hydraulic oil of B cavity is connected with the oil inlet port of solenoid valve through driver housing, the hydraulic oil source of A cavity and B cavity is the oil inlet port of solenoid valve, and the hydraulic oil of A cavity and B cavity flows through driver rotor and driver housing respectively, and is further separated control. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ When the driver is used to drive the rotor blade to rotate clockwise, hydraulic oil is pumped from the hydraulic oil source, flows through the oil inlet, and is communicated with the oil inlet channel A by the control solenoid valve, while the oil inlet channel B is communicated with the solenoid valve drain port; the oil inlet channel A is communicated with the first hydraulic oil channel, and the hydraulic oil flows through the first hydraulic oil channel, the axial oil hole C, the second hydraulic oil channel, the fourth hydraulic oil port, and enters the central hydraulic oil channel, and then flows through the sixth hydraulic oil channel, the seventh hydraulic oil channel and the eighth hydraulic oil channel to enter the corresponding A cavity on the left side of the three blades of the driver rotor respectively, to establish oil pressure and drive the rotor blade to rotate clockwise, while the hydraulic oil in the B cavity flows through the second hydraulic oil port, the third hydraulic oil port and the first hydraulic oil port to the fourth hydraulic oil channel, the fifth hydraulic oil channel and the third hydraulic oil channel, and then flows through the fourth hydraulic oil channel to the oil inlet, and since the oil inlet is communicated with the solenoid valve drain port at this time, the hydraulic oil in the B cavity is rapidly discharged, and the rotor blade is rapidly rotated clockwise. The driver rotor is engaged with the gear on the rotary valve sleeve of the oil control valve through the tooth fan, drives the rotary valve sleeve to rotate, and the rotary valve core of the oil control valve rotates synchronously with the camshaft; the rotary valve core and the rotary valve sleeve are both provided with a matched drain hole, and the relative position of the drain hole of the rotary valve core and the drain hole of the rotary valve sleeve is changed to realize oil discharge at different phases and achieve full variable; The driver for hydraulic drive rotation is used as a kind of hydraulic drive rotating device, and is matched with the FHVVS for use, the rotation of the rotor changes the oil discharge time of the full variable hydraulic valve system, so that the valve timing, valve opening duration and maximum valve lift are continuously variable, thereby improving the power and economy of the internal combustion engine.

2. The fully variable hydraulic valve system of claim 1, wherein, The driver rotor and the driver housing are sealed by a sealing sheet, a sealing groove is formed at the top end of each blade of the driver rotor, a top end sealing sheet is arranged in the sealing groove, the top end sealing sheet is composed of a top end sealing sheet spring, a top end sealing sheet and a side sheet, the sealing of the hydraulic oil is maintained, and the friction surface of the driver housing is cleaned by the elastic force of the top end sealing sheet spring.

3. The fully variable hydraulic valve system of claim 1, wherein, The driver end cover is sealed with the O-shaped sealing ring, an annular groove is formed on the circumferential surface of the end of the driver rotor, and the O-shaped sealing ring is arranged in the annular groove, the sealing ring is tightly attached to the driver end cover, and the sealing of the hydraulic oil is maintained.

4. The fully variable hydraulic valve system of claim 3, wherein, An angle sensor is arranged, the angle sensor and the driver end cover are sealed by the O-shaped sealing ring, an annular sealing groove is formed on the top surface of the driver end cover, and the sealing between the angle sensor and the driver end cover is maintained. The oil inlet channel of the driver housing is sealed by the O-shaped sealing ring, an annular sealing groove is formed on the oil inlet channel, and the O-shaped sealing ring is arranged in the annular sealing groove, so that the sealing of the hydraulic oil is maintained.

5. The fully variable hydraulic valve system of claim 3, wherein, The driver end cover is radially provided with a radial drain hole, the radial drain hole is directly communicated with the external environment, and the excess hydraulic oil directly flows into the external environment through the radial drain hole.

6. A control method of a full variable hydraulic valve system, used in the full variable hydraulic valve system according to any one of claims 1 to 5, characterized by, The cam rotates to drive the rotary valve core of the oil control valve to rotate synchronously. ​ When the radial oil hole of the rotary valve core is rotated to be not communicated with the radial oil hole of the rotary valve sleeve, the oil control valve is in the closed state, the hydraulic tappet driven by the valve cam drives the valve to open, and the oil overcomes the spring force of the valve spring; When the radial oil hole of the rotary valve core is rotated to be not communicated with the radial oil hole of the rotary valve sleeve, the oil control valve is in the closed state, the hydraulic tappet driven by the valve cam drives the valve to open, and the oil overcomes the spring force of the valve spring; When the radial oil hole of the rotary valve core is rotated to be not communicated with the radial oil hole of the rotary valve sleeve, the oil control valve is in the closed state, the hydraulic tappet driven by the valve cam drives the valve to open, and the oil overcomes the spring force of the valve spring; When the radial oil hole of the rotary valve core is rotated to be not communicated with the radial oil hole of the rotary valve sleeve, the oil control valve is in the closed state, the hydraulic tappet driven by the valve cam drives the valve to open, and the oil overcomes the spring force of the valve spring;

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