An automobile engine vibration suppression and monitoring device

Abstract

The present invention relates to a device for suppressing and monitoring the vibration of an automotive engine, belonging to the fields of new energy and vibration control. The engine hood is sleeved on the frame. The side wall of the hood is fixed on the frame seat plate. The frame sleeve of the frame and the frame seat plate form a frame sleeve cavity. A wire frame is arranged outside the frame sleeve, and the wire frame and the frame sleeve form a wire frame cavity; a coil is sleeved outside the wire frame and a wire inner magnet is installed inside; a carrier is installed in the frame sleeve cavity. An axial flow regulating hole is provided on the sliding disk of the carrier, and an internal through valve and a sensor are installed; a lower support spring is arranged between the sliding disk and the frame seat plate, and an upper compression spring is arranged between the sliding disk and the top wall of the hood. The sliding rod of the carrier extends out through the top wall of the hood; the sliding disk divides the frame sleeve cavity into upper and lower cavities, and the upper and lower cavities are connected through the internal through valve and the flow regulating hole. External through valves are provided on the side walls of the upper and lower cavities; a wire outer magnet is arranged on the sliding disk. When the carrier vibrates reciprocally, the wire outer magnet applies a torque to the wire inner magnet and causes it to roll, and the coil cuts the magnetic force lines to generate electricity; the electric energy is supplied to the sensor, the internal through valve and the external through valve for vibration control and monitoring.

Description

Technical Field

[0001] The present invention belongs to the technical fields of new energy and vibration control, and particularly relates to a device for suppressing and monitoring the vibration of an automotive engine, which realizes the regulation and monitoring of engine vibration through vibration energy recovery. Background Art

[0002] Spring shock absorbers have the advantages of simple structure, low cost, and relatively mature technology, and have been widely used in the vibration control of carriers, mechanical equipment, aviation, and navigation. However, due to the non-adjustable damping of traditional spring shock absorbers, their shock absorption effect and environmental adaptability are poor, and they are not suitable for some occasions that require better vibration control effects, such as the vibration isolation of automotive engines and vehicle frames, and the vibration reduction of large precision instrument equipment. Therefore, active and semi-active damping adjustable shock absorbers have been proposed. Compared with traditional single spring shock absorbers, active and semi-active damping adjustable shock absorbers have better control effects and stronger adaptability to vibration environments, and have been applied in certain fields. However, the existing active and semi-active damping adjustment technologies are complex, large in volume, high in manufacturing and use costs, and require continuous external energy supply, which has restricted their popularization and application. Summary of the Invention

[0003] A device for suppressing and monitoring the vibration of an automotive engine according to the present invention is composed of a frame, a hood, a carrier, a lower support spring, an upper compression spring, a circuit board, an external magnet, a coil, an internal magnet, a sensor, an internal communication valve, and an external communication valve. The circuit board is provided with an energy collection, energy management, and energy storage unit.

[0004] In the present invention, the external magnet is installed on the carrier, and the coil and the internal magnet are installed on the frame; or, the external magnet is installed on the frame, and the coil and the internal magnet are installed on the carrier.

[0005] The frame is composed of a frame seat plate, a frame sleeve, and a frame wire frame. One end of the frame sleeve is fixed on the frame seat plate, the frame sleeve is perpendicular to the frame seat plate, and the frame sleeve and the frame seat plate form a frame barrel cavity; the frame wire frame is evenly distributed on the outside of the frame sleeve along the circumferential direction. The cross-section of the frame sleeve is circular or regular polygon. The frame wire frame and the frame sleeve form a wire frame cavity, and the opening of the wire frame cavity is away from the side of the frame sleeve, and the axis of the wire frame cavity is perpendicular to the axis of the frame barrel cavity; when the cross-section of the frame sleeve is a regular polygon, the number of the frame wire frames is equal to the number of sides of the regular polygon of the cross-section of the frame sleeve.

[0006] The hood is sleeved on the frame, the top wall of the hood is pressed against the end of the frame sleeve, the end of the side wall of the hood is fixed on the frame seat plate by screws, and the end of the frame wire frame abuts against the side wall of the hood; the circuit board is installed on the top wall of the hood by screws, and the circuit board is located in the hood cavity.

[0007] A coil is sleeved outside the wire frame, and an in-wire magnet is installed inside. That is, the in-wire magnet is installed in the wire frame cavity. The in-wire magnet is a permanent magnet with a spherical or cylindrical structure. The in-wire magnet is magnetized along the radial direction, and the magnetic poles of the in-wire magnet are distributed along the radial direction. The two magnetic poles are located in the cross-section. The in-wire magnet is located inside the coil, and the wire frame separates the in-wire magnet and the coil. When the in-wire magnet has a cylindrical structure, the axis of the in-wire magnet is perpendicular to the axis of the coil. The axis of the coil coincides with the axis of the wire frame cavity, and the axis of the in-wire magnet is perpendicular to the axis of the holder cylinder cavity. The in-wire magnet can roll freely in the wire frame cavity.

[0008] A carrier is installed in the holder cylinder cavity. The carrier is composed of a sliding disk and a sliding rod. The sliding disk and the sliding rod are perpendicular. A wire hole is provided on the sliding rod, and the wire hole is sealed after the wire is buried. An axial current regulating hole is provided on the sliding disk, and an internal flow valve and a sensor are installed. The internal flow valve is installed at one end of the current regulating hole, and the sensor is used to measure the vibration parameters of the carrier. A lower support spring is provided between the sliding disk and the holder seat plate, and an upper compression spring is provided between the sliding disk and the top wall of the cover. The upper and lower ends of the lower support spring are respectively pressed against the sliding disk and the holder seat plate, and the upper and lower ends of the upper compression spring are respectively pressed against the top wall of the cover and the sliding disk. The upper compression spring is sleeved on the sliding rod, and the sliding rod extends out through the guiding hole on the top wall of the cover. The carrier can move back and forth along the axis. The sliding disk divides the holder cylinder cavity into an upper cavity and a lower cavity. The upper cavity and the lower cavity are connected through the internal flow valve and the current regulating hole. External flow valves are installed on the side walls of the upper cavity and the lower cavity. The internal flow valve and the external flow valve are electric control valves, and the internal flow valve and the external flow valve are piezoelectric or solenoid valves with controllable flow rate and switch.

[0009] At least one cross-section of the sliding disk is provided with an out-wire magnet. The out-wire magnet is an integral ring magnet or a group of sector magnets. A ring magnet can be regarded as a group of sector magnets. When the out-wire magnet is composed of a group of evenly distributed sector magnets, the number of sector magnets is equal to the number of coils and in-wire magnets on the holder sleeve. The sector magnet is magnetized axially or radially, and the ring magnet is magnetized axially or radially. The magnetic poles of the out-wire magnet are distributed along the radial or axial direction of the sliding disk. When the magnetic poles of the out-wire magnet are distributed along the radial and axial directions of the sliding disk, they are respectively called radial out-wire magnets and axial out-wire magnets. The axis of the sliding disk coincides with the axis of the holder cylinder cavity. The magnetic pole configuration of the axially adjacent radial out-wire magnets on the sliding disk is opposite, and the magnetic pole configuration of the axial out-wire magnets is the same.

[0010] The dimension of the out-wire magnet along the axial direction of the carrier is not greater than the diameter of the in-wire magnet, and the diameter of the in-wire magnet is not greater than the conventional amplitude of the carrier. The conventional excitation refers to the minimum value of the amplitude that needs to be controlled and adjusted.

[0011] The number of cross-sections of the out-wire magnet provided on the carrier is odd or even, and the axial distance between the axes of each out-wire magnet is equal, that is, the axial spacing between each group of out-wire magnets along the carrier is equal.

[0012] When not in operation, the external magnets of each group are symmetrically arranged with the plane where the geometric center of the internal magnet of each line is located as the intermediate plane: when the number of groups of external magnets is odd, the geometric center of the middle group of external magnets is coplanar with the geometric center of the internal magnet, and the axial adjacent surface spacing between the two groups of external magnets adjacent to the upper and lower sides of the middle group of external magnets is not less than the diameter of the internal magnet; when the number of groups of external magnets is even, the number of groups of external magnets on the upper and lower sides of the internal magnet is equal, and the distances from the internal magnet to the nearest external magnets on its upper and lower sides are equal, and the axial adjacent surface spacing between the two groups of external magnets is not greater than the diameter of the internal magnet.

[0013] In the present invention, the frame, the hood and the carrier are all made of non-ferromagnetic materials, and the non-ferromagnetic materials include metals such as stainless steel, aluminum alloy and copper or polymer plastics.

[0014] When not in operation, the opposite magnetic poles of the internal magnet and a certain group of external magnets are close to each other and attract each other; when there is vibration in the environment, the carrier vibrates reciprocally along the frame barrel cavity, causing the external magnet and the internal magnet to approach and leave alternately. Each group of external magnets successively applies a rotational torque to the internal magnet. After being acted on by the rotational torque, the internal magnet swings or rolls reciprocally in the wire frame cavity. The magnetic poles of the internal magnet and the magnetic field intensity passing through the coil change alternately. The coil cuts the magnetic force lines and converts mechanical energy into electrical energy. The generated electrical energy is transmitted to the circuit board through a wire, and after being converted and processed, the electrical energy is stored or output to sensors, internal valves and external valves for vibration control and monitoring: the vibration damping and the pressures of the upper cavity and the lower cavity are adjusted by the on-off or flow control of the internal valve and the external valve, thereby adjusting the vibration response characteristics of the system; the sensor obtains the vibration parameters of the system and transmits them through the transmitting unit.

[0015] In the present invention, to obtain better power generation and power supply capabilities, the parameter relationship between the coil x and the internal magnet y of the wire is: λ = L / D = 2 ± 1, δ = T / D = 0.6 ± 0.4, η = V / D = 2.25 ± 0.75, β = H / D = 1.3 ± 0.7, where D is the diameter of the spherical and cylindrical internal magnets of the wire, L is the length of the cylindrical internal magnet of the wire, T, V and H are the wall thickness, radial width and height of the coil respectively. The radial width of the coil refers to the width of the coil along the radial direction of the internal magnet of the wire; δ, η and β are respectively called the coil wall thickness ratio, the coil width ratio and the coil height ratio, and δ, η and β are collectively called the coil parameter ratio; the present invention uses the output power ratio to evaluate the power generation and power supply capabilities. The output power ratio refers to the ratio of the power obtained under different structural parameters to its maximum value, and the output power is the product of the open-circuit voltage and the short-circuit current.

[0016] In the existing spring shock absorber, the damping is non-adjustable, and the vibration control effect and application scenarios are limited. In the existing electromagnetic power generation, a coil cuts the magnetic force lines of a moving magnet located outside the coil to generate electricity. Different from the prior art, the present invention proposes a self-powered damping and stiffness adjustable vibration control and monitoring technology. In its power generation part, an external magnet forces an internal magnet inside the coil to roll, thereby changing the magnetic pole direction and magnetic field intensity of the internal magnet. The coil cuts the magnetic force lines to generate electricity. The function of the external magnet is to drive the internal magnet to rotate and change the magnetic pole direction and magnetic field intensity. The change gradient of the magnetic field intensity generated by the movement of the external magnet is relatively small. During the rolling process of the internal magnet inside the coil, the change gradient of the magnetic field inside the coil caused by the change of the magnetic pole of the internal magnet is large, and the internal magnet rolls multiple times and the coil cuts the magnetic force lines multiple times each time it is excited. Therefore, the power generation ability is strong, the output voltage is high, and the power quantity is large.

[0017] In addition, neither the lower support spring nor the upper compression spring in the present invention is connected to the carrier. During the vibration of the carrier, it only bears the resistance exerted by one of the springs. The equivalent stiffness of the system is low, and it is more suitable for low-frequency and low-intensity vibration scenarios.

[0018] Advantages and features: Combining a mechanical spring with an air spring, improving the vibration suppression effect and realizing the real-time monitoring of the vibration state by adjusting the gas pressure or flow damping; realizing the energy self-sufficiency of the damping adjustment and vibration monitoring system by recycling environmental energy; in the energy recovery unit, using an external magnet to excite the internal magnet inside the coil and make it rotate, increasing the change gradient of the magnetic field intensity by changing the magnetic pole direction of the internal magnet, and realizing multiple cuts of the magnetic force lines to generate electricity in one excitation, with a large power generation quantity and a high output voltage. Brief Description of the Drawings

[0019] Figure 1 is a schematic structural diagram of a vibration suppression and monitoring device using a radial external magnet in a preferred embodiment of the present invention;

[0020] Figure 2 is Figure 1 the A-A cross-sectional view of

[0021] Figure 3 is a schematic structural diagram of a frame in a preferred embodiment of the present invention;

[0022] Figure 4 is Figure 3 the top view of

[0023] Figure 5 is a schematic structural diagram of a machine cover in a preferred embodiment of the present invention;

[0024] Figure 6 is a schematic structural diagram of a vibration suppression and monitoring device using an axial external magnet in a preferred embodiment of the present invention;

[0025] Figure 7 It is a graph showing the relationship between the output power ratio, the coil wall thickness ratio, and the height ratio in a preferred embodiment of the present invention. Detailed implementation manners

[0026] A vibration suppression and monitoring device for an automotive engine according to the present invention is composed of a frame a, a hood b, a carrier c, a lower support spring d, an upper compression spring e, a circuit board p, an external magnetic body w, a coil x, an internal magnetic body y, a sensor q, an internal communication valve u, and an external communication valve v. The circuit board p is provided with an energy harvesting, energy management, and energy storage unit.

[0027] In the present invention, the external magnetic body w is installed on the carrier c, and the coil x and the internal magnetic body y are installed on the frame a; or, the external magnetic body w is installed on the frame a, and the coil x and the internal magnetic body y are installed on the carrier c.

[0028] The frame a is composed of a frame seat plate a1, a frame sleeve a2, and a frame wire frame a4. One end of the frame sleeve a2 is fixed on the frame seat plate a1. The frame sleeve a2 is perpendicular to the frame seat plate a1, and the frame sleeve a2 and the frame seat plate a1 form a frame tube cavity a3. The frame wire frame a4 is evenly distributed on the outside of the frame sleeve a2 in the circumferential direction. The cross-section of the frame sleeve a2 is circular or regular polygon. The frame wire frame a4 and the frame sleeve a2 form a wire frame cavity a5. The opening of the wire frame cavity a5 is away from the side of the frame sleeve a2, and the axis h of the wire frame cavity is perpendicular to the axis i of the frame tube cavity. When the cross-section of the frame sleeve a2 is a regular polygon, the number of the frame wire frames a4 is equal to the number of sides of the polygon of the cross-section of the frame sleeve a2.

[0029] The hood b is sleeved on the frame a. The top wall b1 of the hood is pressed against the end of the frame sleeve a2. The end of the side wall b2 of the hood is fixed on the frame seat plate a1 by screws. The end of the frame wire frame a4 abuts against the side wall b2 of the hood. The circuit board p is installed on the top wall b1 of the hood by screws, and the circuit board p is located in the hood cavity b3.

[0030] The outside of the frame wire frame a4 is sleeved with the coil x, and the internal magnetic body y is installed inside. That is, the internal magnetic body y is installed in the wire frame cavity a5. The internal magnetic body y is a permanent magnet with a spherical or cylindrical structure. The magnetic poles of the internal magnetic body y are distributed radially, that is, the internal magnetic body y is magnetized radially. The internal magnetic body y is located inside the coil x, and the frame wire frame a4 separates the internal magnetic body y and the coil x. When the internal magnetic body y is of a cylindrical structure, the axis f of the internal magnetic body is perpendicular to the axis g of the coil. The axis g of the coil coincides with the axis h of the wire frame cavity, and the axis f of the internal magnetic body is perpendicular to the axis i of the frame tube cavity. The internal magnetic body y can roll freely in the wire frame cavity a5.

[0031] A carrier c is installed in the barrel cavity a3. The carrier c is composed of a sliding disk c1 and a sliding rod c2. The sliding disk c1 and the sliding rod c2 are perpendicular. A wire hole is provided on the sliding rod c2, and the wire hole is sealed after the wire is buried. An axial flow regulating hole c3 is provided on the sliding disk c1, an internal through valve u and a sensor q are installed. The internal through valve u is installed at one end of the flow regulating hole c3. The sensor q is used to measure the vibration parameters of the carrier c. A lower support spring d is provided between the sliding disk c1 and the frame seat plate a1, and an upper compression spring e is provided between the sliding disk c1 and the top wall b1 of the cover. The upper and lower ends of the lower support spring d are respectively pressed against the sliding disk c1 and the frame seat plate a1, and the upper and lower ends of the upper compression spring e are respectively pressed against the top wall b1 of the cover and the sliding disk c1. The upper compression spring e is sleeved on the sliding rod c2, and the sliding rod c2 extends out through the guiding hole on the top wall b1 of the cover. The carrier c can reciprocate axially. The sliding disk c1 divides the barrel cavity a3 into an upper cavity C1 and a lower cavity C2. The upper cavity C1 and the lower cavity C2 are communicated through the internal through valve u and the flow regulating hole c3. External through valves v are installed on the side walls of the upper cavity C1 and the lower cavity C2. The internal through valve u and the external through valve v are electrically controlled valves, and the internal through valve u and the external through valve v are piezoelectric or solenoid valves with controllable flow rate and switch.

[0032] At least one cross-section of the sliding disk c1 is provided with an external magnetic body w outside the wire. The external magnetic body w outside the wire is an integral annular magnet or a group of sector magnets. An annular magnet can be regarded as a group of sector magnets. When the external magnetic body w outside the wire is composed of a group of evenly distributed sector magnets, the number of sector magnets is equal to the number of coils x and internal magnetic bodies y inside the wire on the barrel sleeve a2. The sector magnets are magnetized axially or radially, and the annular magnet is magnetized axially or radially. The magnetic poles of the external magnetic body w outside the wire are distributed along the radial or axial direction of the sliding disk c1. When the magnetic poles of the external magnetic body w outside the wire are distributed along the radial and axial directions of the sliding disk c1, they are respectively called a radial external magnetic body and an axial external magnetic body. The axis of the sliding disk c1 coincides with the axis i of the barrel cavity. The magnetic pole configuration of adjacent radial external magnetic bodies on the sliding disk c1 is opposite, and the magnetic pole configuration of the axial external magnetic bodies is the same.

[0033] The dimension of the external magnetic body w outside the wire along the axial direction of the carrier c is not greater than the diameter of the internal magnetic body y, and the diameter of the internal magnetic body y is not greater than the normal amplitude of the carrier c.

[0034] The number of cross-sections of the external magnetic body w outside the wire provided on the carrier c is odd or even, and the axial distance between the axes of each external magnetic body w outside the wire is equal, that is, the axial spacing between each group of external magnetic bodies w outside the wire along the carrier c is equal.

[0035] When not in operation, the off-line magnets w of each group are symmetrically arranged with the plane where the geometric center of the on-line magnet y of each line lies as the intermediate plane: when the number of axial groups of the off-line magnets w is odd, the geometric center of the middle group of off-line magnets w is coplanar with the geometric center of the on-line magnet y, and the axial adjacent surface spacing between the two groups of off-line magnets w adjacent to the upper and lower sides of the middle group of off-line magnets w is not less than the diameter of the on-line magnet y; when the number of axial groups of the off-line magnets w is even, the number of off-line magnets w on the upper and lower sides of the on-line magnet y is equal, and the distances between the on-line magnet y and the nearest off-line magnets w on its upper and lower sides are equal, and the axial adjacent surface spacing between the two groups of off-line magnets w is not greater than the diameter of the on-line magnet y.

[0036] In the present invention, the frame a, the hood b and the carrier c are all made of non-ferromagnetic materials, and the non-ferromagnetic materials include metals such as stainless steel, aluminum alloy and copper or polymer plastics.

[0037] When not in operation, the opposite magnetic poles of the on-line magnet y and a certain group or a certain off-line magnet w are close to each other and attract each other; when there is vibration in the environment, the carrier c vibrates reciprocally along the frame tube cavity a3, causing the off-line magnet w and the on-line magnet y to approach and leave alternately. Each group of off-line magnets w successively applies a rotational torque to the on-line magnet y. After being acted upon by the rotational torque, the on-line magnet y swings or rolls reciprocally in the wire frame cavity a5. The magnetic poles of the on-line magnet y and the magnetic field intensity passing through the coil x change alternately. The coil x cuts the magnetic force lines and converts mechanical energy into electrical energy. The generated electrical energy is transported to the circuit board p through a wire. After being converted and processed, the electrical energy is stored, or output to the sensor q, the internal through valve u and the external through valve v for vibration control and monitoring: by controlling the on-off or flow rate of the internal through valve u and the external through valve v, the vibration damping and the pressures of the upper cavity C1 and the lower cavity C2 are adjusted, thereby adjusting the vibration response characteristics of the system; the sensor q obtains the vibration parameters of the system and transmits them through the transmitting unit.

[0038] In the present invention, in order to obtain better power generation and supply capabilities, the parameter relationship between the coil x and the on-line magnet y is: λ = L / D = 2 ± 1, δ = T / D = 0.6 ± 0.4, η = V / D = 2.25 ± 0.75, β = H / D = 1.3 ± 0.7, where D is the diameter of the spherical and cylindrical on-line magnet y, L is the length of the cylindrical on-line magnet y, T, V and H are the wall thickness, radial width and height of the coil x respectively. The radial width of the coil x refers to the width of the coil x along the radial direction of the on-line magnet y; δ, η and β are respectively called the coil wall thickness ratio, the coil width ratio and the coil height ratio, and δ, η and β are collectively called the coil parameter ratio; the present invention uses the output power ratio to evaluate the power generation and supply capabilities. The output power ratio refers to the ratio of the power obtained under different structural parameters to its maximum value. The output power is the product of the open circuit voltage and the short circuit current.

[0039] The damping of the existing spring shock absorber is non-adjustable, and the vibration control effect and application scenarios are limited; the existing electromagnetic power generation utilizes a coil to cut the magnetic field lines of a moving magnet located outside the coil; different from the prior art, the present invention proposes a self-powered damping and stiffness adjustable vibration control and monitoring technology. Its power generation part uses an external magnet w to force the internal magnet y of the coil x to roll, thereby changing the magnetic pole direction and magnetic field strength of the internal magnet y of the coil. The coil x cuts the magnetic field lines to generate electricity. The function of the external magnet w is to drive the internal magnet y to rotate and change the magnetic pole direction and magnetic field strength. The change gradient of the magnetic field strength generated by the movement of the external magnet w is relatively small; during the rolling process of the internal magnet y inside the coil x, the change gradient of the magnetic field inside the coil x caused by the change of the magnetic pole of the internal magnet y is large, and the internal magnet y rolls multiple weeks and the coil x cuts the magnetic field lines multiple times each time it is excited. Therefore, the power generation ability is strong, the output voltage is high, and the power is large.

[0040] In addition, neither the lower support spring d nor the upper compression spring e in the present invention is connected to the carrier c. During the vibration of the carrier c, only the resistance applied by one of the springs is borne. The equivalent stiffness of the system is low, and it is more suitable for low-frequency and low-intensity vibration scenarios.

Claims

1. An automobile engine vibration suppression and monitoring device is composed of a frame, a hood, a carrier, a lower support spring, an upper compression spring, a circuit board, an external magnet, a coil, an internal magnet, a sensor, an internal communication valve and an external communication valve. The hood is sleeved on the frame, and the side wall of the hood is fixed on the frame seat plate. The frame sleeve of the frame and the frame seat plate form a frame sleeve cavity. The frame wire frames are evenly distributed along the circumferential direction on the outer side of the frame sleeve, and the frame wire frames and the frame sleeve form a wire frame cavity; A carrier is installed in the frame sleeve cavity. An axial flow regulating hole, an internal communication valve and a sensor are arranged on the sliding disc of the carrier; A lower support spring is arranged between the sliding disc and the frame seat plate, and an upper compression spring is arranged between the sliding disc and the top wall of the hood. The sliding rod of the carrier extends out through the top wall of the hood; The sliding disc divides the frame sleeve cavity into upper and lower cavities, and the upper and lower cavities are communicated through the internal communication valve and the flow regulating hole. External communication valves are installed on the side walls of the upper and lower cavities; It is characterized in that: A coil is sleeved outside the wire frame, and an inner wire magnet is installed inside. The inner wire magnet can roll freely in the wire frame cavity, and the inner wire magnet is located inside the coil; an outer wire magnet is provided on at least one cross-section of the sliding disk; when the carrier vibrates reciprocally, the outer wire magnet and the inner wire magnet approach and leave alternately, the outer wire magnet applies a torque to the inner wire magnet, and the inner wire magnet swings or rolls reciprocally in the wire frame cavity. The coil cuts the magnetic force lines and converts mechanical energy into electrical energy; the electrical energy is stored or output to sensors, an inner communication valve, and an outer communication valve after conversion processing for vibration control and monitoring.

2. The vibration suppression and monitoring device for an automotive engine according to claim 1, wherein: The inner wire magnet is spherical or cylindrical, and the magnetic poles of the inner wire magnet are distributed radially; when the inner wire magnet is of a cylindrical structure, the axis of the inner wire magnet is perpendicular to the axis of the coil.

3. A device for suppressing and monitoring the vibration of an automotive engine according to claim 1, characterized in that: The outer wire magnet is an integral annular magnet or a group of sector magnets. The magnetic poles of the outer wire magnet are distributed radially or axially on the sliding disk. When the magnetic poles of the outer wire magnet are distributed radially and axially on the sliding disk, they are respectively called a radial outer wire magnet and an axial outer wire magnet. The magnetic pole configuration of axially adjacent radial outer wire magnets is opposite, and the magnetic pole configuration of axial outer wire magnets is the same.

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