An inverted single-cylinder cylindrical linear motor active suspension actuator

Abstract

The present invention relates to an inverted single-tube cylindrical linear motor active suspension, which includes a cylindrical linear motor actuator assembly, an inverted single-tube damper assembly, and a helical spring assembly. The cylindrical linear motor actuator assembly consists of a primary assembly with a through-hole of a specific shape and a secondary assembly associated and installed with the primary. The primary assembly includes a winding iron core and a primary outer cylinder, and the structure of the primary iron core is circular ring-shaped; the secondary assembly includes permanent magnets and magnetic conductive rings, and the permanent magnets and the magnetic conductive rings are alternately installed on the side of the damper outer cylinder in sequence, and the magnetic pole direction of each permanent magnet is parallel to the central axis of the damper, and the arrangement method is that the polarities are opposite. While saving installation space and reducing structural complexity, the present invention generates a control force for active control, improves the suspension performance, and at the same time has a Fail-Safe (failure protection) characteristic, retains the basic mechanical structure, ensures that the suspension can still work normally after the motor fails, and improves the vehicle operation stability and driving smoothness.

Description

Technical Field

[0001] The present invention belongs to the technical field of automotive suspension systems, and particularly relates to a cylindrical linear motor type active suspension actuator and an inverted monotube shock absorber. Background Art

[0002] With the development of society and the improvement of people's living standards, people's requirements for the comfort and safety of automobiles are also getting higher and higher. However, the traditional automotive suspension system is limited by its structural characteristics and can only ensure optimal performance under a specific speed and road condition. People have always hoped that the stiffness of the suspension, the damping coefficient of the shock absorber, and the vehicle body height can change with driving conditions such as vehicle load, driving speed, and road surface conditions, so that the suspension can always be near the optimal working state, thereby meeting the requirements for ride comfort, handling stability, etc. of the vehicle. However, many current structures adopt intermediate transmission devices with traditional hydraulic, rack and pinion, and ball screw structures, which increase the transmission energy loss, reduce the response speed and control accuracy of the actuator, and have the disadvantages of high cost, complex structure, low efficiency, unstable operation, high noise, and poor working reliability. Summary of the Invention

[0003] Object of the Invention:

[0004] The present invention provides an inverted monotube cylindrical linear motor active suspension, and its purpose is to solve the problems of high cost, large energy loss, complex structure, and insufficient safety and reliability of existing active suspensions. A novel, compact, and stable electromagnetic active suspension is proposed.

[0005] Technical Solution:

[0006] An inverted monotube cylindrical linear motor active suspension actuator, including a helical spring (3) located between an upper spring support seat (2) and a lower spring support seat (14), characterized in that: it further includes a cylindrical linear motor assembly and a monotube damper assembly that is movably matched with the cylindrical linear motor assembly. The monotube damper assembly is located below the cylindrical linear motor assembly and forms an inverted monotube damper structure with the cylindrical linear motor assembly;

[0007] The cylindrical linear motor assembly includes a primary assembly and a secondary assembly installed inside the primary assembly;

[0008] The primary component includes a winding iron core and a primary outer cylinder (7). The winding iron core includes a three-phase winding (5) and a primary iron core (6). Both the three-phase winding (5) and the primary iron core (6) are distributed inside the primary outer cylinder (7). The three-phase winding is formed by winding the winding coils into a cake shape. The primary iron core (6) is in a circular sheet-like structure. The three-phase winding (5) is arranged between adjacent primary iron cores (6). The three-phase winding (5) and the primary iron core (6) are arranged alternately along the axial direction of the primary outer cylinder (7).

[0009] The secondary component includes a permanent magnet (20) and a magnetic conductive ring (21). The permanent magnet (20) is an axially magnetized ring-shaped permanent magnet structure. The permanent magnet (20) and the magnetic conductive ring (21) are arranged alternately on the outside of the hollow outer cylinder (11). Every two permanent magnets (20) are arranged with opposite polarities. The upper end of the hollow outer cylinder (11) is connected to the upper spring support seat (2).

[0010] The hollow outer cylinder (11) provided with the permanent magnet (20) and the magnetic conductive ring (21) passes through the three-phase winding (5) and the primary iron core (6) and can move relative to the three-phase winding (5) and the primary iron core (6). The primary outer cylinder (7) is located inside the helical spring (3).

[0011] The hollow outer cylinder (11) is a hollow cylinder. The hollow part is a damper cavity. The upper end of the piston rod (16) extends into the damper cavity and is connected to the oil cavity piston (13) inside the damper cavity. The oil cavity piston (13) is a structure that can move along the damper cavity. The oil cavity piston (13) divides the damper cavity into an upper cavity (13-1) and a lower cavity (13-2). A valve port is provided on the oil cavity piston (13). The upper cavity (13-1) and the lower cavity (13-2) perform oil replacement through this valve port.

[0012] A floating piston (12) is further provided inside the hollow outer cylinder (11). The floating piston (12) is located above the oil cavity piston (13). The floating piston (12) is a structure that can move along the axial direction of the hollow outer cylinder (11). A gas cavity (11-1) is formed above the floating piston (12).

[0013] The part of the piston rod (16) extending out of the lower part of the hollow outer cylinder (11) is sleeved with a dust-proof cylinder (17). The lower part of the piston rod (16) is connected to a dust-proof plug (19). The dust-proof plug (19) is connected to the dust-proof cylinder (17). The lower end of the hollow outer cylinder (11) can extend into the dust-proof cylinder (17) and can perform a telescopic action relative to the hollow outer cylinder (11).

[0014] A buffer block (18) is further provided inside the dust-proof cylinder (17). The buffer block (18) is sleeved on the lower part of the piston rod (16).

[0015] There is a raised outer edge (6-1) around the primary iron core (6). During use, the three-phase winding (5) is arranged within the outer edge (6-1), and a wiring opening (6-2) is provided on the outer edge (6-1).

[0016] A positioning groove (6-3) is provided on the outer edge (6-1), and a boss (6-5) that can be snapped into the positioning groove (6-3) is provided at the bottom of the primary iron core (6).

[0017] The primary outer cylinder (7) is connected to the dust-proof cylinder (17).

[0018] The valve port includes a valve port plate (24), and an upper oil hole (22) and a lower oil hole (23) are provided on the valve port plate (24);

[0019] The positions of the upper oil hole (22) and the lower oil hole (23) are staggered. Above the upper oil hole (22), there is a piston valve port upper pressure plate (25), and the piston valve port upper pressure plate (25) is structured to cover the upper oil hole (22) during use and be pushed open by the hydraulic force in the lower chamber (13-2) to open the upper oil hole (22);

[0020] Below the lower oil hole (23), there is a piston valve port lower pressure plate (26), and the piston valve port lower pressure plate (26) is structured to cover the lower oil hole (23) during use and be pushed open by the pressure of the oil in the upper chamber (13-1) to open the lower oil hole (23).

[0021] The lower oil hole (23) is arranged around the upper oil hole (22);

[0022] The center of the valve port plate (24) is connected to a piston rod (16). The piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are arranged on the piston rod (16). The piston valve port upper pressure plate (25) can cover the area where the upper oil hole (22) is located, and the piston valve port lower pressure plate (26) can cover the area where the lower oil hole (23) is located and leave a gap (A) in the area corresponding to the upper oil hole (22).

[0023] The piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are non-elastic plates or elastic plates;

[0024] When the piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are non-elastic plates: The piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are structured to move along the piston rod (16) of the upper valve port pressure plate to control the opening and closing of the upper oil hole (22) and the lower oil hole (23);

[0025] When the piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are elastic plates, the piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) directly cover the upper oil hole (22) and the lower oil hole (23). When the piston valve port upper pressure plate (25) or the piston valve port lower pressure plate (26) is impacted by oil, elastic deformation occurs, so that the upper oil hole (22) or the lower oil hole (23) is opened.

[0026] Advantages and effects:

[0027] With the development of electro-hydraulic control and computer technology, and the improvement of sensors, microprocessors and related manufacturing technologies, human needs have been met, and some active suspensions that can automatically adjust their working states according to the vehicle's driving conditions and load have received widespread attention.

[0028] The present invention is a structure combining a cylindrical linear motor active suspension actuator and an inverted mono-tube shock absorber. The primary component of the cylindrical linear motor actuator cooperates with the secondary component. The primary component includes a winding core and a primary outer cylinder 7. The winding core structure is a three-phase winding 5 and a primary core 6. The three-phase winding 5 is a pancake-shaped annular structure connected to alternating current. Each winding is placed between two primary cores 6. The primary core 6 is an annular sheet structure, which serves as a stator, and the outer ring size matches the inner diameter of the primary outer cylinder 7. The secondary component includes a permanent magnet 20 and a magnetic conductive ring 21. The permanent magnet 20 is an axially magnetized annular shape, and the installation method is that multiple groups of permanent magnets with opposite polarities are mounted on a hollow outer cylinder 11; the magnetic conductive ring 21 is an annular soft iron; the cylindrical hollow outer cylinder 11 is a hollow stainless steel tube; the permanent magnet 20 and the magnetic conductive ring 21 are alternately mounted on the cylindrical hollow outer cylinder 11 in sequence, and the three constitute a mover.

[0029] The primary winding consists of 12 groups of pancake coils, divided into three items: A, B, and C. Each group consists of four windings and is fed with three-phase alternating current.

[0030] The primary core 6 is made of soft iron, and has wiring openings and positioning grooves on its outer diameter, which facilitates the positioning and matching between the winding power supply line and the primary core 6.

[0031] The primary outer cylinder 7 is cylindrical in shape and made of soft iron, and is connected to a lower spring support seat 14 at the bottom to receive the coil spring 3 .

[0032] The upper spring support seat 2 and the lower spring support seat 14 are both processed with grooves. The upper spring support seat 2 is connected to the upper plug 1 by the upper spring support seat connecting bolt 10. The cylindrical hollow outer cylinder 11 is connected to the upper plug 1 by a thread. The lower spring support seat 14 is assembled with the primary outer cylinder 7. The bottom of the primary outer cylinder 7 is located in the groove of the lower spring support seat 14. The lower spring support seat 14 has a wire groove to facilitate the lead-out of the winding power line.

[0033] The helical spring 3 is located outside the actuator composed of the three-phase winding 5, the primary iron core 6, the primary outer cylinder 7, the hollow outer cylinder 11, the permanent magnet 20, and the magnetic conductive ring 21. The helical spring 3 is connected to the actuator through the upper spring support seat 2 and the lower spring support seat 14, and the grooves of the upper spring support seat 2 and the lower spring support seat 14 are used for limiting.

[0034] In the inverted single-tube damper assembly, the upper end of the piston rod 16 has a thread and is threadedly connected to the oil chamber piston 13. The lower end of the piston rod 16 is connected to the dust plug 19 and fixed with a nut. The floating piston 12 and the oil chamber piston 13 divide the cylindrical hollow outer cylinder 11 into a high-pressure gas chamber 11-1 and upper and lower oil chambers 13-1, 13-2. When the cylindrical hollow outer cylinder 11 moves relative to the piston rod 16, the gas in the high-pressure gas chamber 11-1 and the oil in the upper and lower oil chambers 13-1, 13-2 are not replaced and are isolated by the floating piston 12. The oil in the upper and lower oil chambers is replaced through the valve ports on the oil chamber piston 13 under the action of pressure.

[0035] In summary, the cylindrical linear motor type active suspension actuator of the present invention, that is, the inverted single-tube cylindrical linear motor active suspension, has a primary component and a secondary component with a specific structure. The primary component is a winding iron core, which is composed of the three-phase winding 5 and the primary iron core 6. When three-phase alternating current is passed through the three-phase winding 5, a traveling wave magnetic field is generated. At the same time, the secondary component is the permanent magnet 20 and the magnetic conductive ring 21. The permanent magnet 20 is axially magnetized and arranged in an alternating N and S pattern, with a very strong magnetic field. Under the interaction of the traveling wave magnetic field generated by the primary and the magnetic field of the magnet itself, an electromagnetic thrust is generated to drive the cylindrical hollow outer cylinder 11 to perform reciprocating linear motion relative to the primary component. This structural form efficiently utilizes the non-contact advantage of magnetic force transmission, avoids the intermediate transmission devices of traditional hydraulic, gear rack, and ball screw structures, reduces transmission energy loss, and improves the response speed and control accuracy of the actuator, having the advantages of high efficiency, stable operation, low noise, and reliable work.

[0036] The present invention adopts an inverted single-tube damper assembly, which is inverted and improved compared with the previous damper. This is more conducive to the structural arrangement of the primary component and the secondary component, making the structure more compact and enabling more winding iron cores 5 to be arranged, so that the present invention works more efficiently and stably.

[0037] While saving installation space and reducing structural complexity, the present invention generates a control force for active control to improve the suspension performance. At the same time, it has a Fail-Safe (failure protection) characteristic, retains the basic mechanical structure, and ensures that the suspension can still work normally after the motor fails, improving the vehicle operation stability and driving smoothness. Description of the Drawings

[0038] Figure 1Front view vertical sectional structure diagram of the cylinder linear motor type active suspension actuator of the present invention;

[0039] Figure 2 Structure diagram of the primary iron core of the present invention;

[0040] Figure 3 Schematic wiring diagram of the three-phase winding of the present invention;

[0041] Figure 4 Front view vertical sectional structure diagram of the secondary component of the present invention;

[0042] Figure 5 Structural sectional view of the primary iron core;

[0043] Figure 6 Structure diagram of the valve port;

[0044] Figure 7 Structure diagram of the valve port plate;

[0045] Figure 8 Exploded structure diagram of the valve port;

[0046] The names of the parts at each label in the figure are as follows: 1 - upper plug; 2 - upper spring support seat 2; 3 - helical spring; 4 - primary upper cover plate; 5 - three-phase winding; 6 - primary iron core; 7 - primary outer cylinder 7; 8 - primary outer cylinder connecting bolt; 9 - dust-proof cylinder connecting bolt; 10 - upper spring support seat connecting bolt; 11 - cylindrical hollow outer cylinder; 12 - floating piston; 13 - oil chamber piston; 14 - lower spring support seat; 15 - locking nut; 16 - piston rod; 17 - dust-proof cylinder; 18 - buffer block; 19 - dust-proof plug; 20 - permanent magnet; 21 - magnetic conductive ring. Detailed implementation method

[0047] An inverted single-cylinder type cylinder linear motor active suspension actuator, including a helical spring (3) located between an upper spring support seat (2) and a lower spring support seat (14), characterized in that: it further includes a cylinder linear motor assembly and a single-cylinder type damper assembly that is movably matched with the cylinder linear motor assembly. The single-cylinder type damper assembly is located below the cylinder linear motor assembly and forms an inverted single-cylinder type damper structure with the cylinder linear motor assembly;

[0048] The cylinder linear motor assembly includes a primary assembly having the shape of a tooling shaft and a secondary assembly installed inside the primary assembly;

[0049] The primary component includes a winding iron core and a primary outer cylinder (7) (the bottom of the primary outer cylinder (7) is arranged on the lower spring support seat (14)). The winding iron core includes a three-phase winding (5) and a primary iron core (6). The three-phase winding (5) and the primary iron core (6) are both distributed inside the primary outer cylinder (7). The three-phase winding is a winding coil with three terminals connected to three-phase alternating current (leaving three terminals to connect to three-phase alternating current, that is, after the coils are connected, there are three connectors left). The winding coil is wound into a cake shape (each of the 12 windings has two wire ends: the current inlet end (the head end) and the lead-out end (the tail end). Four windings are connected end to end to form a phase. In this way, each phase also has two ends, and then the tail ends of each phase are connected together. In this way, only three head ends are left. See Figure 3 for the wiring schematic diagram). The primary iron core (6) is a circular sheet-like structure (as Figure 2 shown). The three-phase winding (5) is arranged between adjacent primary iron cores (6) (the number of windings is designed, and the size is also designed to ensure that the two ends of the winding iron core are the primary iron cores (6)); the three-phase winding (5) and the primary iron core (6) are arranged alternately along the axial direction of the primary outer cylinder (7). The primary outer cylinder (7) is a column body with an axial through hole, and the whole primary outer cylinder is sleeved on the outside of the assembly of the three-phase winding (5) and the primary iron core (6).

[0050] The secondary component includes a permanent magnet (20) and a magnetic conduction ring (21). The permanent magnet (20) is an axially magnetized ring-shaped permanent magnet structure. The permanent magnet (20) and the magnetic conduction ring (21) are arranged alternately on the outside of the cylindrical hollow outer cylinder (11) (the permanent magnet (20) and the magnetic conduction ring (21) are arranged alternately along the axial direction of the hollow outer cylinder (11)). Every two permanent magnets (20) are arranged with opposite polarities. The magnetic conduction ring (21) is a ring-shaped iron sheet structure and is installed together with the permanent magnet 20 on the outside of the cylindrical hollow outer cylinder 11. The cylindrical hollow outer cylinder 11 is a cylindrical hollow column body, and the two ends are processed with internal threads and are respectively connected to the helical spring assembly and the inverted single-cylinder damper assembly. The upper end of the hollow outer cylinder (11) is connected to the upper spring support seat (2);

[0051] The hollow outer cylinder (11) provided with the permanent magnet (20) and the magnetic conduction ring (21) passes through the three-phase winding (5) and the primary iron core (6) and can move axially relative to the three-phase winding (5) and the primary iron core (6); the primary outer cylinder (7) is located inside the helical spring (3);

[0052] The cylindrical hollow outer cylinder (11) is a hollow cylinder, and the hollow part is the damper cavity. The upper end of the piston rod (16) extends into the damper cavity and is connected to the oil chamber piston (13) in the damper cavity through a thread. The oil chamber piston (13) is a structure that can move along the axial direction of the damper cavity. The lower end of the piston rod (16) is connected with a dust-proof plug (19) through a thread. The oil chamber piston (13) divides the damper cavity into an upper chamber (13-1) and a lower chamber (13-2). A valve port is provided on the oil chamber piston (13), and the upper chamber (13-1) and the lower chamber (13-2) perform oil replacement through this valve port.

[0053] A floating piston (12) is further provided in the hollow outer cylinder (11). The floating piston (12) is located above the oil chamber piston (13). The floating piston (12) is a structure that can move along the axial direction of the hollow outer cylinder (11) (i.e., Figure 1 the up-and-down direction in

[0054] That is to say: This application has a floating piston 12 and an oil chamber piston 13, forming a gas chamber and upper and lower oil chambers 13-1 and 13-2. The gas chamber is isolated from the oil chamber (upper chamber (13-1)) through the floating piston 12, and the upper and lower oil chambers perform oil replacement through the valve port of the oil chamber piston 13 on the piston rod 12.

[0055] The spiral spring assembly includes an upper spring support seat 2 connected to the secondary assembly, a lower spring support seat 14 connected to the primary assembly, a dust-proof cylinder, and a spiral spring 3.

[0056] The part of the lower portion of the piston rod (16) extending out of the hollow outer cylinder (11) is sleeved with a dust-proof cylinder (17) (the part of the lower portion of the piston rod (16) extending out of the hollow outer cylinder (11) passes through the dust-proof cylinder or the part of the lower portion of the piston rod (16) extending out of the hollow outer cylinder (11) is located inside the dust-proof cylinder (17)). The lower portion of the piston rod (16) is connected with a dust-proof plug (19) through a thread. The dust-proof plug (19) is connected to the dust-proof cylinder (17). The lower end of the hollow outer cylinder (11) can extend into the dust-proof cylinder (17) and can perform telescopic movement relative to the hollow outer cylinder (11) (along the axial direction of the hollow outer cylinder (11), i.e., Figure 1 the up-and-down direction in

[0057] A buffer block (18) is further provided in the dust-proof cylinder (17). The buffer block (18) is sleeved on the lower portion of the piston rod (16). (Such as Figure 1As shown, the buffer block (18) is located above the dust-proof plug (19) at the inner bottom of the dust-proof cylinder (17). When the actuator exceeds the working range, the lower end of the hollow outer cylinder (11) will hit the dust-proof plug (19). Therefore, to prevent exceeding the range, the buffer block (18) slows down the impact and plays a role in protecting the components)

[0058] There is a raised outer edge (6-1) around the primary iron core (6). In use, the three-phase winding (5) is arranged inside the outer edge (6-1), and a wiring port (6-2) is provided on the outer edge (6-1). (The wiring port (6-2) is for the three-phase winding (5) to route wires. During processing, the four ports are convenient for positioning and processing. Secondly, according to the actual equipment situation, three of them can be selected for wiring, and the other one is reserved).

[0059] A positioning groove (6-3) is provided on the outer edge (6-1), and a boss (6-5) that can be inserted into the positioning groove (6-3) is provided at the bottom of the primary iron core (6).

[0060] The primary outer cylinder (7) is connected to the dust-proof cylinder (17) by connecting bolts 9.

[0061] The upper spring support seat 2 is connected to the upper plug 1 by the upper spring support seat connecting bolt 10, and the upper plug 1 blocks the top of the hollow outer cylinder (11);

[0062] The lower spring support seat 14 is connected to the primary outer cylinder 7 by the primary outer cylinder connecting bolt 8. The support seats are all formed by stamping steel plates. The helical spring 3 is located between the upper spring support seat 2 and the lower spring support seat 14.

[0063] The described valve port includes a valve port plate (24), and an upper oil hole (22) and a lower oil hole (23) are provided on the valve port plate (24);

[0064] The upper oil hole (22) and the lower oil hole (23) are arranged with their positions staggered. Above the upper oil hole (22), there is a piston valve port upper pressing plate (25). The piston valve port upper pressing plate (25) is a structure that can cover the upper oil hole (22) during use and can be pushed open by the oil pressure in the lower cavity (13-2) to open the upper oil hole (22);

[0065] Below the lower oil hole (23), there is a piston valve port lower pressing plate (26). The piston valve port lower pressing plate (26) is a structure that can cover the lower oil hole (23) during use and can be pushed open by the oil pressure in the upper cavity (13-1) to open the lower oil hole (23).

[0066] The lower oil hole (23) is arranged around the upper oil hole (22) (the upper oil hole (22) is arranged around the center of the valve port plate (24), and the lower oil hole (23) is arranged around the upper oil hole (22) as Figure 7 shown);

[0067] The center of the valve port plate (24) is connected to the piston rod (16). The upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) are arranged on the piston rod (16). The upper piston valve port pressing plate (25) can cover the area where the upper oil hole (22) is located. The lower piston valve port pressing plate (26) can cover the area where the lower oil hole (23) is located and leave a gap (A) in the area corresponding to the upper oil hole (22); (As Figure 8 shown, the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) are arranged on the piston rod (16). To prevent the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) from rotating, an anti-rotation key (16-1) can be arranged on the piston rod (16). Of course, it doesn't matter if the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) rotate, because the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) can both be set to be circular. No matter how they rotate, the covered and left areas remain unchanged. Since the upper oil hole (22) is arranged along the circumference of the piston rod (16), the area of the upper piston valve port pressing plate (25) only needs to be able to cover this area. And since the lower oil hole (23) is arranged around the upper oil hole (22), the structure of the lower piston valve port pressing plate (26) is different from that of the upper piston valve port pressing plate (25). As Figure 8 shown, a collar (26-1) sleeved on the piston rod (16) is arranged in the middle of the lower piston valve port pressing plate (26). The collar is connected to the outer plate (26-3) through a connecting rib (26-2). The connecting rib (26-2) avoids the area where the upper oil hole (22) is located. The area between the collar (26-1) and the outer plate (26-3) is the area corresponding to the upper oil hole (22), and this area is the reserved gap (A). That is to say, the position of the upper oil hole (22) is avoided at this gap (A). Of course, there can also be other existing connection methods, which will not be elaborated here.)

[0068] The upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) are non-elastic plates or elastic plates;

[0069] When the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) are non-elastic plates: The upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) are structures that can move along the piston rod (16) of the upper valve port pressing piece (parallel) to control the opening and closing of the upper oil hole (22) and the lower oil hole (23); (This movement doesn't need to be too large. The movement distance of the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26) is restricted by a limit nut screwed on the piston rod (16) of the upper valve port pressing piece. The opening and closing of the upper oil hole (22) and the lower oil hole (23) are controlled by the movement of the upper piston valve port pressing plate (25) and the lower piston valve port pressing plate (26))

[0070] When the piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) are elastic plates: the piston valve port upper pressure plate (25) and the piston valve port lower pressure plate (26) directly cover the upper oil hole (22) and the lower oil hole (23). When the piston valve port upper pressure plate (25) or the piston valve port lower pressure plate (26) is impacted by oil, elastic deformation occurs to open the upper oil hole (22) or the lower oil hole (23). (There is not much displacement, it depends on the elastic deformation of the pressure plate, similar to the oil squeezing the pressure plate, the pressure plate is subjected to a certain amount of warping; when the impact force disappears, it automatically returns to its original position.)

[0071] The technical solution in the embodiment of the present invention will be further described below in conjunction with the accompanying drawings in the embodiment of the present invention:

[0072] Figure 1 This is a schematic diagram of the vertically placed structure of the cylindrical linear motor active suspension actuator of the present invention, which is a front view section. The embodiment includes: 1-upper plug; 2-upper spring support seat 2; 3-coil spring 3; 4-primary upper cover plate (covering the upper end of the primary outer cylinder 7); 5-three-phase winding; 6-primary iron core; 7-primary outer cylinder 7; 8-primary outer cylinder 7 connecting bolts; 9-dustproof cylinder connecting bolts; 10-upper spring support seat connecting bolts; 11-cylindrical hollow outer cylinder; 12-floating piston; 13-oil chamber piston; 14-lower spring support seat 14; 15-locking nut; 16-piston rod; 17-dustproof cylinder; 18-buffer block; 19-dustproof plug.

[0073] The coil spring 3 assembly includes an upper spring support seat 2, a lower spring support seat 14 and a coil spring 3. The upper spring support seat 2 and the lower spring support seat 14 are circular steel plates with grooves, which are made by stamping. The upper spring support seat 2 is connected and fixed to the upper plug 1 by a connecting bolt 10, and the lower spring support seat 14 is connected and fixed to the primary outer cylinder 7 by a primary outer cylinder connecting bolt 8. The lower spring support seat 14 is connected and fixed to the dust cylinder 17 by a dust cylinder connecting bolt 9. The coil spring 3 is placed between the upper and lower spring support seats to complete the combined assembly of the coil spring assembly.

[0074] The cylindrical linear motor assembly includes a primary assembly having a tooling shaft shape and a secondary assembly installed inside the primary assembly (the upper plug 1 will be connected to the vehicle body through other components, the secondary assembly will be indirectly connected to the upper plug 1, the dust cover 17 will be connected to the wheel, and the primary assembly will be indirectly connected to the dust cover 17. When the vehicle is driving, the vehicle body and the wheel will move relative to each other, thereby driving the primary and secondary assemblies to move relative to each other).

[0075] The primary component includes a winding iron core and a primary outer cylinder. The winding iron core consists of a three-phase winding 5 and a primary iron core 6. The primary outer cylinder 7 has a through-hole structure and is integrally sleeved outside the winding iron core. The upper primary cover plate 4 is fixedly connected to the primary outer cylinder 7 by bolts to ensure the fixation of the upper end of the winding iron core. The lower spring support seat 14 connected to the primary outer cylinder 7 assembles and fixes the lower end position of the winding iron core, thus completing the combined assembly of the primary component.

[0076] The primary iron core 6 inside the winding iron core has an annular structure with square keys processed on it. The outer diameter of the annulus matches that of the primary outer cylinder 7. The shape of the primary iron core 6 is like Figure 3 , and to prevent conductivity, the outer layer of the entire primary iron core 6 is coated with insulating paint. The three-phase winding is a winding coil, and its winding shape is disc-shaped. The connection method is as Figure 1 shown, and it is alternately installed with the primary iron core 7 in sequence, as Figure 3 shown. There are a total of 12 groups. Every four groups are connected to form one phase. The windings A-1, A-2, A-3, A-4 are phase A, the windings B-1, B-2, B-3, B-4 are phase B, and the windings C-1, C-2, C-3, C-4 are phase C. A1, B1, C1 are the leading ends of each phase winding. The trailing ends of each phase winding are connected together, leaving a total of three ports A1, B1, C1 (that is, after connecting the three phases A, B, C, a total of three ports A1, B1, C1 are left) to be connected to the external power supply. The windings are connected to three-phase alternating current. Each group of coils is wrapped with a layer of polyimide film for insulation (the lead wires also need to be coated, but a certain length needs to be left uncoated for connecting to the power supply), and insulating thermal conductive silicone grease is applied to conduct heat and facilitate heat dissipation.

[0077] The secondary component is coaxially installed in the hole of the primary component. The secondary component includes a permanent magnet 20 and a magnetic conductive ring 21, as Figure 4 shown. The permanent magnet 20 has an annular shape and adopts an axial magnetization form. The magnetic conductive ring 21 is a soft iron ring with an annular shape. During the combined assembly, the upper and lower permanent magnets 20 are installed in a way that the magnetic poles repel each other, and the permanent magnet 20 and the magnetic conductive ring 21 are alternately installed in sequence, that is, a magnetic conductive ring 21 is arranged between every two permanent magnets 20. The permanent magnet 20 and the magnetic conductive ring 21 are sleeved on the cylindrical hollow outer cylinder 11. The upper end of the cylindrical hollow outer cylinder 11 has been machined with a shoulder to play a fixing role at the upper end, and the lower end has been machined with an external thread and assembled with a locking nut 15 to play a fixing role at the lower end, thus completing the combined assembly of the secondary component. When the cylindrical linear motor component works, the primary component and the secondary component will perform relative reciprocating motion. At this time, electromagnetic thrust is output using the principle of electromagnetic induction.

[0078] The inverted single-tube damper assembly includes a cylindrical hollow outer tube 11, a floating piston 12, an oil chamber piston 13, a piston rod 16, and a dust-proof tube 17. The upper plug 1 has an external thread for connecting to the cylindrical hollow outer tube 11. The floating piston 12 and the oil chamber piston 13 divide the cylindrical hollow outer tube 11 into a high-pressure gas chamber and upper and lower oil chambers. The floating piston 12 completely isolates the gas from the oil, and they do not communicate with each other. The pressures of both the gas and the oil are preset within a certain range to ensure the normal operation of the actuator. The oil chamber piston 13 is provided with a valve port, which will open when the pressure received by the valve port reaches the set value, allowing the oil in the upper and lower oil chambers to flow and exchange with each other. When the primary component and the secondary component move relative to each other, both the high-pressure gas and the oil will be compressed under pressure. When the relative movement speed is small, the high-pressure gas is first compressed for buffering. At this time, the pressure is not enough to open the valve port, and no oil exchange occurs. When the relative speed is large, at this time, the pressure received by the high-pressure gas reaches the set maximum value, and the buffering effect is limited. Then the valve port opens, and the oil in the upper and lower oil chambers is exchanged. The buffering is carried out by relying on the damping force of the oil flowing through the valve port.

[0079] In summary, during use:

[0080] Embodiment 1: This embodiment is the structure without the floating piston 12. When the primary component and the secondary component move relative to each other, the helical spring 3 is compressed. At this time, the oil in the upper chamber (13-1) is compressed. When the relative movement speed is small, the pressure is not enough to open the valve port, and no oil exchange occurs. When the relative speed is large, the valve port opens, and the oil in the upper chamber (13-1) and the lower chamber (13-2) is exchanged. The buffering is carried out by relying on the damping force of the oil flowing through the valve port.

[0081] Embodiment 2 (in this working condition, when the impact received by the suspension is small, it can be buffered by its own damping, and at this time the actuator can be used for energy harvesting and power generation. It can rely on gas first and then oil): This embodiment is the structure with the floating piston 12. When the helical spring 3 is compressed, both the high-pressure gas in the gas chamber (11-1) and the oil in the upper chamber (13-1) will be compressed under pressure. When the relative movement speed is small, the high-pressure gas is first compressed for buffering. At this time, the pressure is not enough to open the valve port, and no oil exchange occurs. When the relative speed is large, at this time, the pressure received by the high-pressure gas reaches the set maximum value, and the buffering effect is limited. Then the valve port opens, and the oil in the upper chamber (13-1) and the lower chamber (13-2) is exchanged. The buffering is carried out by relying on the damping force of the oil flowing through the valve port. The cylindrical linear motor assembly does not need to provide active power. However, at this time, there is still a relatively small relative movement between the primary component and the secondary component. It can rely on its own magnetic field to generate an induced current and store and utilize it.

[0082] Embodiment 3 (in this condition, when the impact on the suspension is greater, the linear motor provides the active force): When the relative speed is greater than that in Embodiment 2, the helical spring 3 is compressed. Due to the flow hysteresis of the oil in the upper chamber (13-1) and the lower chamber (13-2), it is not sufficient to provide damping force quickly for effective buffering. At this time, a certain value of current Ⅰ needs to be passed through the cylindrical linear motor assembly (the specific value needs to be calculated by the vehicle controller according to the actual impact situation). By relying on the magnetic field to generate electromagnetic force, the active force Ⅰ is provided to accelerate the compression speed and improve the buffering ability, but no induced current is generated at this time. After that, because the helical spring 3 is compressed greatly, it will accelerate the stretching and rebounding. The damping force of the oil exchange between the upper chamber (13-1) and the lower chamber (13-2) is not sufficient to control the rebounding speed. At this time, a certain value of current Ⅱ needs to be passed through the cylindrical linear motor assembly, and the electromagnetic force is generated by relying on the magnetic field to provide the active force Ⅱ to control the rebounding speed (to avoid excessive rebounding speed and excessive vibration of the vehicle).

[0083] Embodiment 4 (in this condition, the suspension needs to provide a large supporting force to cope with the body attitude changes under the conditions of sharp turns, rapid acceleration, and sudden braking, and the linear motor provides the active force): When the damping force of the inverted monotube damper assembly itself is not sufficient to support the helical spring 3 from being compressed to provide effective supporting force, a certain value of current Ⅲ needs to be passed through the cylindrical linear motor assembly at this time. By relying on the magnetic field to generate electromagnetic force, the active force Ⅲ is provided to provide additional supporting force.

Claims

1. An inverted single-cylinder linear motor active suspension actuator, comprising a helical spring (3) located between an upper spring support seat (2) and a lower spring support seat (14). Characterized in that: It further includes a cylinder linear motor assembly and a single-cylinder damper assembly that is movably matched with the cylinder linear motor assembly; the single-cylinder damper assembly is located below the cylinder linear motor assembly to form an inverted single-cylinder damper structure with the cylinder linear motor assembly. The cylinder linear motor assembly includes a primary assembly and a secondary assembly installed inside the primary assembly. The primary assembly includes a winding iron core and a primary outer cylinder (7). The winding iron core includes a three-phase winding (5) and a primary iron core (6). The three-phase winding (5) and the primary iron core (6) are both distributed inside the primary outer cylinder (7). The three-phase winding is wound into a cake shape by winding coils. The primary iron core (6) is a circular sheet-like structure. The three-phase winding (5) is arranged between adjacent primary iron cores (6); the three-phase winding (5) and the primary iron core (6) are alternately arranged along the axial direction of the primary outer cylinder (7). The secondary assembly includes a permanent magnet (20) and a magnetic conductive ring (21). The permanent magnet (20) is an axially magnetized ring-shaped permanent magnet structure. The permanent magnet (20) and the magnetic conductive ring (21) are alternately arranged on the outside of the hollow outer cylinder (11). Every two permanent magnets (20) are arranged with opposite polarities. The upper end of the hollow outer cylinder (11) is connected to the upper spring support seat (2). The hollow outer cylinder (11) passes through the three-phase winding (5) and the primary iron core (6) and can move relative to the three-phase winding (5) and the primary iron core (6); the primary outer cylinder (7) is located inside the helical spring (3). The hollow outer cylinder (11) is a hollow cylinder. The hollow part is a damper cavity. The upper end of the piston rod (16) extends into the damper cavity and is connected to an oil cavity piston (13) inside the damper cavity. The oil cavity piston (13) is a structure that can move along the damper cavity. The oil cavity piston (13) divides the damper cavity into an upper cavity (13-1) and a lower cavity (13-2). A valve port is provided on the oil cavity piston (13). The upper cavity (13-1) and the lower cavity (13-2) perform oil replacement through this valve port. A floating piston (12) is further provided inside the hollow outer cylinder (11). The floating piston (12) is located above the oil cavity piston (13). The floating piston (12) is a structure that can move along the axial direction of the hollow outer cylinder (11). A gas cavity (11-1) is formed above the floating piston (12). A protruding outer edge (6-1) is provided around the primary iron core (6). During use, the three-phase winding (5) is arranged inside the outer edge (6-1), and a wiring port (6-2) is provided on the outer edge (6-1).

2. An inverted single-cylinder linear motor active suspension actuator according to claim 1. Characterized in that: A dust-proof cylinder (17) is sleeved on the part of the lower part of the piston rod (16) that extends out of the hollow outer cylinder (11). A dust-proof plug (19) is connected to the lower part of the piston rod (16). The dust-proof plug (19) is connected to the dust-proof cylinder (17). The lower end of the hollow outer cylinder (11) can extend into the dust-proof cylinder (17) and can perform a telescopic action relative to the hollow outer cylinder (11).

3. An inverted single-cylinder linear motor active suspension actuator according to claim 2, characterized in that: A buffer block (18) is further arranged in the dust-proof cylinder (17), and the buffer block (18) is sleeved on the lower part of the piston rod (16).

4. An inverted single-cylinder linear motor active suspension actuator according to claim 1, characterized in that: A positioning groove (6-3) is arranged on the outer edge (6-1), and a convex platform (6-5) capable of being clamped into the positioning groove (6-3) is arranged at the bottom of the primary iron core (6).

5. An inverted single-cylinder linear motor active suspension actuator according to claim 1, characterized in that: The primary outer cylinder (7) is connected to the dust-proof cylinder (17).

6. An inverted single-cylinder linear motor active suspension actuator according to claim 1, characterized in that: The valve port includes a valve port plate (24), and an upper oil hole (22) and a lower oil hole (23) are arranged on the valve port plate (24); The upper oil hole (22) and the lower oil hole (23) are arranged with their positions staggered from each other. A piston valve port upper pressing plate (25) is arranged above the upper oil hole (22). The piston valve port upper pressing plate (25) is a structure that can cover the upper oil hole (22) during use and can be pushed open by the oil pressure in the lower cavity (13-2) to open the upper oil hole (22); A piston valve port lower pressing plate (26) is arranged below the lower oil hole (23). The piston valve port lower pressing plate (26) is a structure that can cover the lower oil hole (23) during use and can be pushed open by the oil pressure in the upper cavity (13-1) to open the lower oil hole (23).

7. An inverted single-cylinder linear motor active suspension actuator according to claim 6, characterized in that: The lower oil hole (23) is arranged around the upper oil hole (22); The center of the valve port plate (24) is connected to the piston rod (16). The piston valve port upper pressing plate (25) and the piston valve port lower pressing plate (26) are arranged on the piston rod (16). The piston valve port upper pressing plate (25) can cover the area where the upper oil hole (22) is located, and the piston valve port lower pressing plate (26) can cover the area where the lower oil hole (23) is located and leave a gap (A) in the area corresponding to the upper oil hole (22).

8. An inverted single-cylinder linear motor active suspension actuator according to claim 6, characterized in that: The piston valve port upper pressing plate (25) and the piston valve port lower pressing plate (26) are non-elastic plates or elastic plates; When the piston valve port upper pressing plate (25) and the piston valve port lower pressing plate (26) are non-elastic plates: the piston valve port upper pressing plate (25) and the piston valve port lower pressing plate (26) are structures that can move along the piston rod of the upper valve port pressing plate (16) to control the opening and closing of the upper oil hole (22) and the lower oil hole (23); When the upper pressing plate (25) and the lower pressing plate (26) of the piston valve port are elastic plates: The upper pressing plate (25) and the lower pressing plate (26) of the piston valve port directly cover the upper oil hole (22) and the lower oil hole (23). When the upper pressing plate (25) or the lower pressing plate (26) of the piston valve port is impacted by the oil fluid, elastic deformation occurs, causing the upper oil hole (22) or the lower oil hole (23) to open.

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