Driver driven to rotate hydraulically, fully variable hydraulic valve system and control method

Abstract

The invention provides a hydraulically-driven rotating driver, a fully-variable hydraulic valve system and a control method, and belongs to the technical field of hydraulic driving. The hydraulically-driven rotating driver comprises a driver shell, a driver rotor and an electromagnetic valve; the driver shell and the driver rotor form a hydraulic cavity; a driver rotor and an electromagnetic valve are mounted on the driver shell; each blade of the driver rotor divides a hydraulic cavity formed by the driver shell and the driver rotor into a left part and a right part, the hydraulic cavity formed on the left side of the blade is defined as a cavity A, and the hydraulic cavity formed on the right side of the blade is defined as a cavity B; hydraulic oil is controlled to flow in and out of different channels based on the electromagnetic valves, and a pressure difference is established between the cavity A and the cavity B of the rotor blade, so that the driver rotor is driven to rotate.

Description

Technical Field

[0001] The present invention belongs to the technical field of hydraulic drive, and in particular relates to a hydraulically driven rotating driver, a fully variable hydraulic valve system and a control method. Background Art

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

[0003] In order to further optimize the internal combustion engine related technologies, researchers have developed a fully variable hydraulic valve system that can achieve continuous changes in valve timing, valve opening duration and valve maximum lift. However, the existing system has problems such as high cost, overly complex system composition and poor response performance.

[0004] The control of the valve movement law of the fully variable hydraulic valve system is achieved by controlling the connection and disconnection of the high-pressure oil chamber and the low-pressure oil chamber in the hydraulic system. The oil leakage phase of the oil control valve between the high-pressure oil chamber and the low-pressure oil chamber is mostly controlled by a motor. However, due to the limitations of its own mechanical and physical properties, if it is actually applied on an internal combustion engine, higher requirements are placed on the overall oil leakage 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 installed in the housing, a hydraulic accumulator and a transmission mechanism. It is a fully variable hydraulic valve system oil control device that can replace high-frequency solenoid valves and is applied to single-cylinder and multi-cylinder internal combustion engines.

[0006] In terms of control method, the device drives the rotary valve sleeve to rotate through a servo motor driving the rack meshing with the rotary valve sleeve gear, changing the circumferential position of the radial oil hole on the rotary valve sleeve and thus changing the oil leakage time. However, the servo motor is too large, expensive, and has a temperature tolerance of only 80°C, which makes actual control applications difficult. Summary of the invention

[0007] In order to overcome the deficiencies of the above-mentioned prior art, the present invention provides a hydraulically driven rotating driver, a fully variable hydraulic valve system and a control method, which can change the oil leakage time of the fully variable hydraulic valve system by rotating the rotor, so as to achieve the purpose of continuously variable valve timing, valve opening duration and valve maximum 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: In a first aspect, a hydraulically driven rotational driver is disclosed, comprising: Driver housing, driver rotor and solenoid valve; The driver housing and the driver rotor form a hydraulic chamber; the driver rotor and the solenoid valve are installed on the driver housing; Each blade of the driver rotor divides the hydraulic chamber formed by the driver housing and the driver rotor into two parts, 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; The solenoid valve controls the inflow and outflow of hydraulic oil in different channels, thereby establishing a pressure difference between the A cavity and the B cavity of the rotor blade, thereby driving the drive rotor to rotate.

[0009] As a further technical solution, the driver housing is provided with a plurality of hydraulic oil channels, an axial oil hole C and a plurality of hydraulic oil ports; 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; The solenoid valve is provided with an oil inlet passage.

[0010] As a further technical solution, each of the A cavities is in communication with a corresponding hydraulic oil channel on the driver rotor, and the hydraulic oil channel is in communication with the central hydraulic oil channel, and a hydraulic oil port is provided on the central hydraulic oil channel; The hydraulic oil port is communicated with the second hydraulic oil channel of the 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 solenoid valve oil inlet port through the solenoid valve oil inlet channel.

[0011] As a further technical solution, each of the B chambers is communicated with the corresponding hydraulic oil port on the drive housing, the 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 of the solenoid valve through the oil inlet channel of the solenoid valve.

[0012] As a further technical solution, a sealing plate is used to seal the driver rotor and the driver housing. A sealing groove is opened at the top of each blade of the driver rotor. A top sealing plate is installed in the sealing groove. The top sealing plate consists of a top sealing plate spring, a top sealing plate and a side plate to maintain the sealing of the hydraulic oil and clean the friction surface of the driver housing through the elastic force of the top sealing plate spring.

[0013] As a further technical solution, it also includes a driver end cover, which is sealed with an O-ring at the end of the driver rotor. 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 sealing ring is tightly attached to the driver end cover to maintain the sealing of the hydraulic oil.

[0014] 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. The top surface of the driver end cover is provided with an annular sealing groove to maintain the seal between the angle sensor and the driver end cover.

[0015] As a further technical solution, an O-ring is used to seal the oil inlet channel at the oil inlet of the driver housing and the hydraulic oil source. The oil inlet channel is provided with an annular sealing groove, and an O-ring is installed in the annular sealing groove to maintain the sealing of the hydraulic oil.

[0016] As a further technical solution, the driver end cover is radially provided with a radial oil drain hole, the radial oil drain hole is directly connected to the external environment, and the excess hydraulic oil directly flows into the outside through the radial oil drain hole.

[0017] In a second aspect, a fully variable hydraulic valve system is disclosed, comprising: Hydraulically driven rotating actuator, oil control valve; The hydraulically driven rotating driver at least comprises a driver rotor, and the oil control valve comprises a rotary valve core and a rotary valve sleeve; The driver rotor meshes with the gear on the rotary valve sleeve of the oil control valve through the gear fan, driving 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 matched oil drain holes. By changing the relative positions of the oil drain holes of the rotary valve core and the oil drain holes of the rotary valve sleeve, oil drain is achieved at different phase moments, thereby achieving full variability.

[0018] In a third aspect, a control method of a fully variable hydraulic valve system is disclosed, comprising: The rotation of the valve cam drives the rotary valve core of the oil control valve to rotate synchronously; When the radial oil hole of the rotary valve core rotates to be disconnected from the radial oil hole of the rotary valve sleeve, the oil control valve is in a 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; 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 starts to leak oil, and the valve is closed; When the system oil leakage phase needs to be changed, the switch of the solenoid valve is controlled to drive the driver rotor to rotate. The gear fan on the driver rotor rotates synchronously with the driver rotor, driving the gear on the rotary valve sleeve of the oil control valve to rotate, thereby driving the rotary valve sleeve of the oil control valve to rotate. The circumferential position of the radial oil hole of the rotary valve sleeve also changes accordingly, thereby changing the oil leakage phase of the oil control valve, achieving the purpose of controlling the valve timing, valve opening duration and valve lift to be fully variable.

[0019] As a further technical solution, the hydraulic oil used during oil leakage comes from the lubrication system of the internal combustion engine itself.

[0020] One or more of the above technical solutions have the following beneficial effects: The technical solution of the present invention controls the inflow and outflow of hydraulic oil in different channels by controlling the solenoid valve, and establishes a pressure difference on both sides of the swing cylinder rotor blade, thereby driving the rotor to rotate and achieving the purpose of hydraulic drive rotation. The rotating device is used in combination with FHVVS, and the oil leakage 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 valve maximum lift, thereby greatly improving the power and economy of the internal combustion engine.

[0021] The technical solution of the present invention can replace the servo motor as the oil leakage drive device in the fully variable hydraulic valve system, and its structure is compact and has better temperature resistance. The overall sealing effect of the technical solution of the present invention is good, and the sealing method such as the top sealing sheet is adopted to reduce the leakage of hydraulic oil. The hydraulically driven rotating driver of the technical solution of the present invention has good scalability and great application potential, and can be used as a hydraulically driven rotating device in related technical fields.

[0022] Advantages of additional aspects of the present invention will be given in part in the following description, and in part will become obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The accompanying drawings in the specification, which constitute a part of the present invention, are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute improper limitations on the present invention.

[0024] Figure 1 A schematic cross-sectional view of the overall structure of an example embodiment of the present invention; Figure 2 A schematic cross-sectional view of the structure of a sub-driver housing according to an embodiment of the present invention; Figure 3 Example of the present invention Figure 2 BB cross-section diagram; Figure 4 Example of the present invention Figure 2 CC profile of ; Figure 5 It is a schematic cross-sectional view of the structure of the sub-driver rotor according to an embodiment of the present invention; Figure 6 Example of the present invention Figure 5 AA section view; Figure 7 It is a schematic cross-sectional view of the structure of the sub-driver end cover according to an embodiment of the present invention. In the figure, 1. angle sensor, 2. first O-ring, 3. driver end cover, 4. second O-ring, 5. driver rotor, 6. driver housing, 7. needle bearing, 8. third O-ring, 9. solenoid valve, 10. first hydraulic oil channel, 11. axial oil hole C, 12. second hydraulic oil channel, 13. first hydraulic oil port, 14. third hydraulic oil channel, 15. second hydraulic oil port, 16. fourth hydraulic oil channel, 17. third hydraulic oil port, 18. fifth hydraulic oil channel, 19. oil inlet, 20. oil return port, 21. fourth hydraulic oil port, 22. central hydraulic oil channel, 23. sixth hydraulic oil channel, 24. seventh hydraulic oil channel, 25. eighth hydraulic oil channel, 26. radial oil drain hole. DETAILED DESCRIPTION

[0025] It should be noted that the following detailed descriptions are exemplary and are intended to provide further explanation of the present invention. Unless otherwise specified, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art to which the present invention belongs.

[0026] It should be noted that the terms used herein are for describing specific embodiments only and are not intended to be limiting of exemplary embodiments according to the present invention.

[0027] In the absence of conflict, the embodiments of the present invention and the features of the embodiments may be combined with each other.

[0028] Terminology explanation: Needle roller bearing: It is a roller bearing with cylindrical rollers. The rollers are thin and long relative to their diameter. This type of roller is called a needle roller. Despite its small cross-section, the bearing still has a high load-bearing capacity. Needle roller bearings are equipped with thin and long rollers (roller diameter D≤5mm, L / D≥2.5, L is the roller length), so the radial structure is compact. When its inner diameter size and load capacity are the same as those of other types of bearings, the outer diameter is the smallest, which is particularly suitable for support structures with limited radial installation dimensions.

[0029] Embodiment 1 This embodiment discloses a hydraulically driven rotating driver, including a driver housing 6 , a driver end cover 3 , a driver rotor 5 , an angle sensor 1 and a solenoid valve 9 .

[0030] It should be noted that the hydraulically driven rotation driver can be applied to a hydraulic engine.

[0031] See attached Figure 2As 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 and an oil return port 20, and a needle bearing 7, and the needle bearing 7 is located on the driver rotor 5.

[0032] The driver end cover 3 is composed of screw holes, rotor mounting holes, annular sealing grooves and radial oil drain holes 26. Figure 7 The schematic cross-sectional view of the drive 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 where the first O-ring 2 is installed, i.e. Figure 7 The largest circle with the lowest center. Radial oil drain hole Figure 7 Already marked.

[0033] The driver rotor 5 is composed of a fourth hydraulic oil 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, a second sealing groove and a third sealing groove, etc., see the attached Figure 5 , Figure 6 shown.

[0034] The solenoid valve 9 includes an oil inlet passage and an oil return passage, wherein the oil inlet passage and the oil return passage of the solenoid valve 9 are connected to the oil return passage of the solenoid valve 9. Figure 2 The oil inlet 19 and the oil return port 20 of the middle driver housing 6 are connected, and the position of the channel inside the solenoid valve can be changed, and the specific channel position relationship of the solenoid valve will not be described in detail.

[0035] 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 left and right parts. 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.

[0036] Each A cavity is communicated with the corresponding sixth hydraulic oil channel 23, seventh hydraulic oil channel 24 and eighth hydraulic oil channel 25 on the driver rotor 5. The sixth hydraulic oil channel 23, seventh hydraulic oil channel 24 and eighth hydraulic oil channel 25 are communicated with the central hydraulic oil channel 22. The central hydraulic oil channel 22 is provided with a fourth hydraulic oil port 21. The fourth hydraulic oil port 21 is communicated with the second hydraulic oil channel 12 of the driver housing 6. The second hydraulic oil channel 12 is communicated with the first hydraulic oil channel 10 through the axial oil hole C11. The first hydraulic oil channel 10 receives the hydraulic oil from the oil inlet 19 of the solenoid valve 9 through the oil inlet channel of the solenoid valve 9. The pressure of the hydraulic cavity can be controlled more flexibly in the above manner.

[0037] Each B chamber is communicated with the corresponding second hydraulic oil port 15, the third hydraulic oil port 17 and the first hydraulic oil port 13 on the drive housing 6, the second hydraulic oil port 15, the third hydraulic oil port 17 and the first hydraulic oil port 13 are communicated with the corresponding fourth hydraulic oil channel 16, the fifth hydraulic oil channel 18 and the third hydraulic oil channel 14, and the fourth hydraulic oil channel 16 receives hydraulic oil from the oil inlet 19 of the solenoid valve 9 through the oil inlet channel of the solenoid valve 9.

[0038] Among them, although the hydraulic oil sources of chamber A and chamber B are ultimately the oil inlet 19 of the solenoid valve 9, their channels flow through the driver rotor 5 and the driver housing 6 respectively, and are controlled separately without interfering with each other, and the controllability is better.

[0039] In order to achieve the sealing of the overall equipment, a sealing plate is used to seal between the driver rotor 5 and the driver housing 6. A first sealing groove, a second sealing groove and a third sealing groove are opened at the top of each blade of the driver rotor 5. Top sealing plates are installed in the above sealing grooves. The top sealing plates are made of cast iron treated with electron beams to improve the wear resistance of the friction surface. The top sealing plates are composed of top sealing plate springs, top sealing plates and side plates to maintain the sealing of the hydraulic oil and clean the friction surface of the driver housing 6 through the elastic force of the top sealing plate springs.

[0040] The driver end cover 3 and the end of the driver rotor 5 are sealed by a first O-ring 2. Specifically, an annular sealing groove is opened on the circumferential surface of the end of the driver 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 driver end cover 3 to maintain the sealing of the hydraulic oil.

[0041] A second O-ring 4 is used to seal between the angle sensor 1 and the driver end cover 3. An annular sealing groove is provided on the top surface of the driver end cover 3. 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, thereby ensuring the accuracy of the angle sensor.

[0042] A third O-ring 8 is used to seal the oil inlet channel at the oil inlet port 19 of the driver housing 6 and the hydraulic oil source. An annular sealing groove is provided in the oil inlet channel, and a third O-ring 8 is installed in the annular sealing groove to maintain the sealing of the hydraulic oil and ensure sufficient supply of hydraulic oil.

[0043] The driver end cover 3 is radially provided with a radial oil drain hole 26 , which is directly connected to the external environment, and the excess hydraulic oil directly flows into the external environment, such as the oil pan, through the radial oil drain hole 26 .

[0044] The working process of the present invention is described below: When the hydraulically driven rotating driver of the present invention is used to drive the rotor blades to rotate clockwise, the 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 the oil inlet channel B is connected to the oil drain port of the solenoid valve. The oil inlet channel A is connected with the first hydraulic oil channel 10. The hydraulic oil flows through the first hydraulic oil channel 10, the axial oil hole C11, the second hydraulic oil channel 12, and the fourth hydraulic oil port 21 into the central hydraulic oil channel 22, and respectively enters the corresponding A hydraulic chambers on the left sides 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 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 to the fourth hydraulic oil channel 16, the fifth hydraulic oil channel 18 and the third hydraulic oil channel 14 through the second hydraulic oil port 15, the third hydraulic oil port 17 and the first hydraulic oil port 13, and then flows to the oil inlet 19 through the fourth hydraulic oil channel 16. Since the oil inlet 19 is the same as the oil drain port of the solenoid valve at this time, the hydraulic oil in the B chamber is quickly discharged, and the rotor blades are quickly rotated clockwise. In this way, a quick response to working conditions can be achieved, and the responsiveness is better.

[0045] When the hydraulically driven rotating driver in this embodiment drives the rotor blades to rotate counterclockwise, the hydraulic oil is pumped out from the hydraulic oil source, flows through the oil inlet 19, and the oil inlet 19 is connected to the oil inlet channel B by controlling the solenoid valve, and the oil inlet channel A is connected to the oil drain hole of the solenoid valve. The oil inlet channel B is connected with the fourth hydraulic oil channel 16. The hydraulic oil flows through the fourth hydraulic oil channel 16, the fifth hydraulic oil channel 18 and the third hydraulic oil channel 14, and respectively enters the corresponding B-type hydraulic chambers on the right sides 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 to establish oil pressure and drive the rotor to rotate counterclockwise. At this time, the hydraulic oil in the A chamber flows to the second hydraulic oil channel 12 through the sixth hydraulic oil channel 23, the seventh hydraulic oil channel 24 and the eighth hydraulic oil channel 25, and then flows to the first hydraulic oil channel 10. The first hydraulic oil channel 10 is connected with the oil inlet 19. Since the oil inlet 19 is the same as the oil drain port of the solenoid valve at this time, the hydraulic oil in the A chamber is quickly discharged, and the rotor blades are quickly rotated counterclockwise, which can achieve a quick response to working conditions and better responsiveness.

[0046] In this embodiment, the pressure balance of the hydraulic oil in the A chamber and the B chamber is further achieved by controlling the solenoid valve, so that the rotor blades can maintain their unchanged position.

[0047] Embodiment 2 The purpose of this embodiment is to provide a fully variable hydraulic valve system, including: Hydraulically driven rotating actuator and oil control valve; The hydraulically driven rotating driver comprises at least a driver rotor 5, and the oil control valve comprises a rotary valve core and a rotary valve sleeve; The driver rotor 5 meshes with the gear on the rotary valve sleeve of the oil control valve through the gear fan, driving 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 matching oil drain holes. By changing the relative positions of the oil drain holes of the rotary valve core and the oil drain holes of the rotary valve sleeve, oil drain can be achieved at different phase moments, thereby achieving full variability.

[0048] In this embodiment, the hydraulically driven rotating driver not only includes the driver rotor 5, but also includes the above-mentioned housing, end cover, solenoid valve, etc.

[0049] When in application, the hydraulically driven rotating driver of the embodiment of the present invention can be used as an oil leakage angle control device of a fully variable hydraulic valve system. The driver rotor meshes with the gear on the rotary valve sleeve of the oil control valve in the fully variable hydraulic valve system through the gear fan, driving the rotary valve sleeve to rotate. The rotary valve core of the oil control valve rotates synchronously with the camshaft. Matching oil leakage holes are provided on the valve core and the valve sleeve. By changing the relative positions of the valve core oil leakage hole and the valve sleeve oil leakage hole, oil leakage is achieved at different phase moments to achieve full variability. Specifically, when the oil leakage holes of the valve core and the valve sleeve do not overlap, no oil leakage occurs; when the valve core rotates to overlap with the oil leakage hole of the valve sleeve, oil leakage occurs.

[0050] In this embodiment, when the hydraulically driven rotating driver is working, the driver rotor is driven to rotate by controlling the switch of the solenoid valve, and the gear fan on the driver rotor rotates synchronously with the driver rotor. The gear of the oil control valve sleeve is meshed with the gear fan on the driver, so that the rotary valve sleeve of the oil control valve rotates, and the valve core rotates synchronously with the camshaft, and the relative positions of the two change.

[0051] Embodiment 3 The purpose of this embodiment is to provide a control method for a fully variable hydraulic valve system, including: When the fully variable hydraulic valve system is working, the valve 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 rotates to be disconnected from the radial oil hole of the rotary valve sleeve, the oil control valve is in a closed state, and the valve cam drives the hydraulic support to establish high pressure in the hydraulic chamber. The high-pressure oil overcomes the elastic force of the valve spring to drive 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 oil control valve is in an open state, the system starts to leak oil, and the valve is closed.

[0052] When the system oil leakage phase needs to be changed, the hydraulically driven rotating driver of the present invention is in a working state, and the driver rotor is driven to rotate by controlling the switch of the solenoid valve. The gear fan on the driver rotor rotates synchronously with the driver rotor, driving the gear on the rotary valve sleeve of the oil control valve to rotate, thereby driving the rotary valve sleeve of the oil control valve to rotate, and the circumferential position of the radial oil hole of the rotary valve sleeve also changes accordingly, thereby changing the oil leakage phase of the oil control valve, achieving the purpose of controlling the valve timing, the valve opening duration and the valve lift to be fully variable.

[0053] Therefore, under the effect of the present invention, different oil leakage moments can be controlled according to different internal combustion engine operating conditions, thereby realizing flexible control of the valve movement law of the internal combustion engine.

[0054] The oil leakage control device of the present embodiment, i.e., the hydraulically driven rotating driver, plays a role in controlling the oil leakage law between the hydraulic drive device of the fully variable hydraulic valve system and the low-pressure system. The oil leakage law can be flexibly controlled within a certain range. The present invention can also play a sealing role with good sealing effect, which reduces the leakage of hydraulic oil and greatly improves the control accuracy of the valve movement law. It has a wide range of applications and can meet the requirements of various operating conditions of the internal combustion engine.

[0055] When the driver of the example of this embodiment is used as an oil leakage driver of a fully variable hydraulic valve system, the hydraulic oil used comes from the lubrication system of the internal combustion engine itself.

[0056] Although the above describes the specific implementation mode of the present invention in conjunction with the accompanying drawings, it 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 on the basis of the technical solution of the present invention without creative work are still within the scope of protection of the present invention.

Claims

1. A hydraulically driven rotary actuator characterized by: include: Driver housing, driver rotor and solenoid valve; The driver housing and the driver rotor form a hydraulic chamber; the driver rotor and the solenoid valve are installed on the driver housing; Each blade of the driver rotor divides the hydraulic chamber formed by the driver housing and the driver rotor into two parts, 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; The solenoid valve controls the inflow and outflow of hydraulic oil in different channels, thereby establishing a pressure difference between the A cavity and the B cavity of the rotor blade, thereby driving the drive rotor to rotate.

2. The hydraulically driven rotary actuator according to claim 1, characterized in that: The driver housing is provided with a plurality of hydraulic oil channels, an axial oil hole C and a plurality of hydraulic oil ports; 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; The solenoid valve is provided with an oil inlet passage.

3. The hydraulically driven rotary actuator according to claim 2, characterized in that: Each of the A cavities is in communication with a corresponding hydraulic oil channel on the driver rotor, and the hydraulic oil channel is in communication with the central hydraulic oil channel, and a hydraulic oil port is provided on the central hydraulic oil channel; The hydraulic oil port is communicated with the second hydraulic oil channel of the 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 solenoid valve oil inlet port through the solenoid valve oil inlet channel.

4. The hydraulically driven rotary actuator according to claim 2, characterized in that: Each of the B chambers is communicated with a corresponding hydraulic oil port on the driver housing, and the hydraulic oil port is communicated with a corresponding hydraulic oil channel. The fourth hydraulic oil channel receives hydraulic oil from the oil inlet port of the solenoid valve through the oil inlet channel of the solenoid valve.

5. The hydraulically driven rotary actuator according to claim 1, characterized in that: The driver rotor and the driver housing are sealed with a sealing plate. A sealing groove is opened at the top of each blade of the driver rotor. A top sealing plate is installed in the sealing groove. The top sealing plate consists of a top sealing plate spring, a top sealing plate and a side plate to maintain the sealing of the hydraulic oil and clean the friction surface of the driver housing through the elastic force of the top sealing plate spring.

6. The hydraulically driven rotary actuator according to claim 1, characterized in that: It also includes a driver end cover, which is sealed with an O-ring at the end of the driver rotor. An annular groove is opened on the circumferential surface of the driver rotor end, and an O-ring is installed in the annular groove. The sealing ring is tightly attached to the driver end cover to maintain the sealing of the hydraulic oil.

7. The hydraulically driven rotary actuator according to claim 6, characterized in that: It also includes an angle sensor, wherein an O-ring is used to seal the angle sensor and the driver end cover, and an annular sealing groove is provided on the top surface of the driver end cover to maintain the seal between the angle sensor and the driver end cover; An O-ring is used to seal the oil inlet channel at the oil inlet of the driver housing and the hydraulic oil source. An annular sealing groove is provided in the oil inlet channel, and an O-ring is installed in the annular sealing groove to maintain the sealing of the hydraulic oil.

8. The hydraulically driven rotary actuator according to claim 6, characterized in that: The driver end cover is radially provided with a radial oil drain hole, which is directly connected to the external environment, and the excess hydraulic oil directly flows into the outside through the radial oil drain hole.

9. Fully variable hydraulic valve system, characterized by: include: The hydraulically driven rotating actuator according to any one of claims 1 to 8, and the oil control valve; The hydraulically driven rotating driver at least comprises a driver rotor, and the oil control valve comprises a rotary valve core and a rotary valve sleeve; The driver rotor meshes with the gear on the rotary valve sleeve of the oil control valve through the gear fan, driving 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 matched oil drain holes. By changing the relative positions of the oil drain holes of the rotary valve core and the oil drain holes of the rotary valve sleeve, oil drain is achieved at different phase moments, thereby achieving full variability.

10. A control method for a fully variable hydraulic valve system, used in the fully variable hydraulic valve system according to claim 9, characterized in that: include: The rotation of the valve cam drives the rotary valve core of the oil control valve to rotate synchronously; When the radial oil hole of the rotary valve core rotates to be disconnected from the radial oil hole of the rotary valve sleeve, the oil control valve is in a closed state, the valve cam drives the hydraulic pressure to stay in the hydraulic chamber, and the oil overcomes the elastic force of the valve spring to drive 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 oil control valve is in the open state, the system starts to leak oil, and the valve is closed; When the system oil leakage phase needs to be changed, the switch of the solenoid valve is controlled to drive the driver rotor to rotate. The gear fan on the driver rotor rotates synchronously with the driver rotor, driving the gear on the rotary valve sleeve of the oil control valve to rotate, thereby driving the rotary valve sleeve of the oil control valve to rotate. The circumferential position of the radial oil hole of the rotary valve sleeve also changes accordingly, thereby changing the oil leakage phase of the oil control valve, achieving the purpose of controlling the valve timing, valve opening duration and valve lift to be fully variable.

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