A multi-mode controllable inertia damping device for high-mobility vehicles

Abstract

The present invention discloses a multi-mode controllable inertia damping device for a high-mobility vehicle, comprising an upper lifting lug, a cylinder disposed below the upper lifting lug, a piston mechanism disposed within the cylinder, a lower lifting lug disposed below the piston mechanism, a hydraulic motor disposed outside the cylinder, a rotary motor, and an electromagnetic clutch disposed above the rotary motor. The inner wall of the cylinder is provided with two upper and lower flow channels connecting the oil inlet and oil outlet of the hydraulic motor with the upper and lower chambers of the cylinder. The output shaft of the hydraulic motor is connected to the rotor shaft of the rotary motor, which is connected to the driving shaft of the electromagnetic clutch. The driven shaft of the electromagnetic clutch is fixedly connected to the flywheel. The piston mechanism passes through the lower end of the cylinder and is fixedly connected to the lower lifting lug. The upper lifting lug is fixedly connected to the upper end of the cylinder. The present invention has the beneficial effect of realizing an integrated design of the complex structure and multi-mode control of the high-mobility vehicle inertia suspension, effectively broadening the control range and dynamic boundaries of the high-mobility vehicle suspension system.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle suspension, in particular to a multi-mode controllable inertia damping device for a high-mobility vehicle. Background Art

[0002] Because high-mobility vehicles often travel on rough and harsh roads, the road inputs they experience on their suspension systems are characterized by large and long-lasting impact loads. This limits the ride smoothness and off-road maneuverability of these vehicles, which are limited by the vibration isolation performance of the suspension system. Therefore, an inertia device is introduced into the suspension system of high-mobility vehicles. This device utilizes the mass characteristics of the inertia device to achieve tuned dissipation of suspension vibration energy, thereby improving the vehicle's off-road maneuverability.

[0003] However, existing mechanical inertia sensors, such as ball screw and rack-and-pinion types, are passive devices. Under high impact loads, they can experience backlash, deformation, and friction, making them difficult to meet the operating requirements of high-mobility vehicle suspension systems. Furthermore, mechanical inertia sensors have simple impedance characteristics, making it impossible to achieve continuous adjustment of the inertia coefficient or coordinated control of inertia, damping, and complex impedance.

[0004] In view of the above situation, it is necessary to improve the defects of the existing mechanical inertia container so that it can adapt to the current needs of using inertia containers. Summary of the Invention

[0005] The purpose of the present invention is to overcome the problem of mechanical inertia container parameters being unable to be adjusted and the problem of coordinated control of inertia force, damping force and complex impedance, and to realize mode switching among active, energy feeding and coordinated control.

[0006] The technical solution of the present invention for achieving the above-mentioned purpose is a multi-mode controllable inertia damping device for high-mobility vehicles, comprising an upper lifting ear, a cylinder arranged below the upper lifting ear, a piston mechanism arranged in the cylinder, a lower lifting ear arranged below the piston mechanism, a hydraulic motor arranged on the outside of the cylinder, a rotating motor, and an electromagnetic clutch arranged above the rotating motor. Two upper and lower flow channels are provided on the inner wall of the cylinder to connect the oil inlet and oil outlet of the hydraulic motor with the upper and lower chambers of the cylinder. The output shaft of the hydraulic motor is connected to the rotor shaft of the rotating motor, the rotor shaft of the rotating motor is connected to the driving shaft of the electromagnetic clutch, the driven shaft of the electromagnetic clutch is fixedly connected to the flywheel, the piston mechanism passes through the lower end of the cylinder and is fixedly connected to the lower lifting ear, and the upper lifting ear is fixedly connected to the upper end of the cylinder.

[0007] As a further supplement to the present technical solution, the piston mechanism includes a piston housing arranged in the cylinder, a piston upper cover arranged in the piston housing, a piston rod arranged at the lower end of the piston housing, and a sliding valve assembly arranged in the piston housing. The piston upper cover is fixedly installed at the upper end of the piston housing, the sliding valve assembly is fixedly installed at the lower end of the piston housing, the center of the piston upper cover is opened, the piston rod is fixedly connected to the lower lifting ear, and a circular hole is opened between the sliding valve assembly and the piston housing.

[0008] As a further supplement to the present technical solution, the piston rod, the piston and the cylinder are aligned with each other in the axis direction and the piston and the piston rod have the freedom of linear motion relative to the cylinder.

[0009] As a further supplement to the present technical solution, the sliding valve assembly includes a sliding valve support, a sliding valve arranged on the sliding valve support, a sliding valve winding arranged below the sliding valve, and a sliding valve spring arranged below the sliding valve. The sliding valve support is fixedly connected to the lower end of the piston housing, a circular hole is provided between the sliding valve support and the piston housing, the sliding valve winding is fixedly surrounded inside the sliding valve support, one end of the sliding valve spring is fixedly connected to the sliding valve, and the other end thereof is fixedly connected to the sliding valve support.

[0010] As a further supplement to the technical solution, the axes of the sliding valve and the sliding valve support are aligned, and the sliding valve and the sliding valve support have the freedom of relative linear movement.

[0011] As a further supplement to the present technical solution, the lower end of the piston upper cover matches the shape of the upper end of the sliding valve and fits tightly when the two are covered.

[0012] As a further supplement to the present technical solution, the electromagnetic clutch also includes an electromagnetic clutch housing, an active disk arranged inside the electromagnetic clutch housing, and a driven disk arranged above the active disk. The active disk is fixed inside the electromagnetic clutch housing, and the active disk, the electromagnetic clutch housing, and the rotor of the rotating motor have the freedom of rotational movement. The driven shaft is arranged on the driven disk, and a clutch spring is nested on the outside of the driven shaft. One end of the clutch spring is fixedly connected to the driven shaft, and the other end thereof is fixedly connected to the driven disk; a clutch winding is fixed around the inside of the driven disk.

[0013] As a further supplement to the present technical solution, the clutch spring is aligned with the axis of the driven shaft, the driven shaft has a degree of freedom of rotational motion relative to the housing, and the driven shaft has a degree of freedom of linear motion relative to the driven disk.

[0014] Its beneficial effects are that the present invention proposes a multi-mode controllable inertia damping device for high-mobility vehicles, which controls the damping force output by controlling the current of the sliding valve winding to change the sliding valve opening, thereby controlling the damping force output and realizing continuous adjustment of the device's damping coefficient; by controlling the current of the clutch winding in the electromagnetic clutch, the coupling pressure between the driven plate and the active plate is adjusted, thereby changing the friction torque, controlling the inertia force output and realizing continuous adjustment of the device's inertia coefficient; and by connecting a rotating motor to different external end networks, it is possible to realize working modes such as "passive control", "energy feedback control" and "active control" of the rotating motor; at the same time, the "passive control" and "energy feedback control" of the rotating motor can be coordinated with the "semi-active control" of the inertia damping to realize coordinated matching between the inertia force, damping force and electrical network impedance; the present invention realizes the integrated design of the complex structure of the inertia suspension of high-mobility vehicles and multi-mode control, effectively broadening the control range and dynamic boundaries of the suspension system of high-mobility vehicles. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is a schematic diagram of the overall structure of a multi-mode controllable high-mobility vehicle inertia damping device according to the present invention;

[0016] Figure 2 It is a structural schematic diagram of the electromagnetic clutch of the present invention;

[0017] Figure 3 It is a structural schematic diagram of the piston mechanism of the present invention;

[0018] In the figure, 1. flywheel; 2. electromagnetic clutch housing; 3. rotating motor; 4. hydraulic motor; 5. oil; 6. upper lifting eye; 7. cylinder; 8. piston housing; 9. piston rod; 10. lower lifting eye; 11. driven shaft; 12. driven plate; 13. driving plate; 14. clutch spring; 15. clutch winding; 16. piston upper cover; 17. sliding valve support; 18. sliding valve winding; 19. sliding valve; 20. sliding valve spring. DETAILED DESCRIPTION

[0019] In order to make the technical solution more clear to those skilled in the art, Figure 1-3 The technical solution of the present invention is described in detail:

[0020] like Figure 1-3As shown, the technical solution adopted by the present invention is a multi-mode controllable high-mobility vehicle inertia damping device, including an upper lifting ear 6, a cylinder 7 arranged below the upper lifting ear 6, a piston mechanism arranged in the cylinder 7, a lower lifting ear 10 arranged below the piston mechanism, a hydraulic motor 4 arranged on the outside of the cylinder 7, a rotating motor 3, and an electromagnetic clutch arranged above the rotating motor 3. The inner wall of the cylinder 7 is provided with two upper and lower flow channels to connect the oil inlet and oil outlet of the hydraulic motor 4 with the upper chamber and lower chamber of the cylinder 7. The output shaft of the hydraulic motor 4 is connected to the rotor shaft of the rotating motor 3, the rotor shaft of the rotating motor 3 is connected to the driving shaft of the electromagnetic clutch, the driven shaft 11 of the electromagnetic clutch is fixedly connected to the flywheel 1, the piston mechanism passes through the lower end of the cylinder 7 and is fixedly connected to the lower lifting ear 10, and the upper lifting ear 6 is fixedly connected to the upper end of the cylinder 7.

[0021] The structure of the piston mechanism will be described in detail below. The piston mechanism includes a piston housing 8 arranged in the cylinder 7, a piston upper cover 16 arranged in the piston housing 8, a piston rod 9 arranged at the lower end of the piston housing 8, and a sliding valve assembly arranged in the piston housing 8. The piston upper cover 16 is fixedly mounted on the upper end of the piston housing 8, and the sliding valve assembly is fixedly mounted on the lower end of the piston housing 8. The center of the piston upper cover 16 is opened, the piston rod 9 is fixedly connected to the lower ear 10, and a circular hole is opened between the sliding valve assembly and the piston housing 8, wherein the piston rod 9 and the axis of the cylinder 7 are aligned and the piston and the piston rod 9 have the freedom of linear motion relative to the cylinder 7; wherein the sliding valve 19 assembly includes a sliding valve support The seat 17, the sliding valve 19 arranged on the sliding valve support 17, the sliding valve winding 18 arranged below the sliding valve 19, and the sliding valve spring 20 arranged below the sliding valve 19, the sliding valve support 17 is fixedly connected to the lower end of the piston housing 8, a circular hole is opened between the sliding valve support 17 and the piston housing 8, the sliding valve winding 18 is fixedly surrounded by the inside of the sliding valve support 17, one end of the sliding valve spring 20 is fixedly connected to the sliding valve 19, and the other end thereof is fixedly connected to the sliding valve support 17, the axes of the sliding valve 19 and the sliding valve support 17 are aligned, and the sliding valve 19 and the sliding valve support 17 have the freedom of relative linear motion; the lower end of the piston upper cover 16 matches the shape of the upper end of the sliding valve 19 and the two fit tightly when covered.

[0022] Among them, the specific structure of the electromagnetic clutch also includes an electromagnetic clutch housing 2, an active disk 13 arranged inside the electromagnetic clutch housing 2, and a driven disk 12 arranged above the active disk 13. The active disk 13 is fixed inside the electromagnetic clutch housing 2, and the active disk 13 and the electromagnetic clutch housing 2 and the rotor of the rotating motor 3 have the freedom of rotational motion. The driven shaft 11 is arranged on the driven disk 12, and a clutch spring 14 is nested on the outside of the driven shaft 11. One end of the clutch spring 14 is fixedly connected to the driven shaft 11, and the other end thereof is fixedly connected to the driven disk 12; a clutch winding 15 is fixed around the inside of the driven disk 12; the clutch spring 14 is aligned with the axis of the driven shaft 11, and the driven shaft 11 has the freedom of rotational motion relative to the electromagnetic clutch housing 2, and the driven shaft 11 has the freedom of linear motion relative to the driven disk 12.

[0023] Among them, when the upper lifting ear 6 and the lower lifting ear 10 move linearly relative to each other, the piston rod 9 and the piston are driven to move linearly relative to the cylinder 7. The oil 5 inside the cylinder 7 flows into the interior of the piston through the central opening of the piston upper cover 16, and flows out through the circular hole between the piston housing 8 and the sliding valve support 17 after passing through the sliding valve 19, so as to realize the flow of oil 5 in the upper and lower chambers of the cylinder 7, thereby generating a damping force; at the same time, the piston pushes the oil 5 through the flow channel on the inner wall of the cylinder 7 into the hydraulic motor 4, and the flow of oil 5 drives the output shaft of the hydraulic motor 4 to rotate, and drives the rotor of the rotating motor 3 and the electromagnetic clutch housing 2 to rotate.

[0024] Among them, the sliding valve spring 20 in the piston is initially in a compressed state. When no current flows through the sliding valve winding 18, the sliding valve 19 is tightly fitted with the piston cover 16 under the thrust of the sliding valve spring 20, and the oil 5 cannot flow through the piston; when current flows through the sliding valve winding 18, the sliding valve winding 18 generates electromagnetic force, pushing the sliding valve 19 to perform linear motion relative to the sliding valve support 17; by controlling the current size, the size of the gap between the sliding valve 19 and the piston cover 16 can be changed, thereby controlling the damping force generated when the oil 5 flows through the piston.

[0025] Among them, the clutch spring 14 in the electromagnetic clutch is initially in a compressed state. When no current flows through the clutch winding 15, the driven disc 12 is fully in contact with the driving disc 13 under the thrust of the clutch spring 14. When the rotating motor 3 drives the electromagnetic clutch housing 2 to rotate, the friction torque is transmitted to the driven disc 12 through the driving disc 13, thereby driving the driven shaft 11 and the flywheel 1 to rotate, realizing inertia packaging and outputting inertial force; when current flows through the clutch winding 15, the clutch winding 15 generates electromagnetic force, pushing the driven disc 12 to perform linear motion relative to the driving disc 13. By controlling the current size, the contact pressure between the driven disc 12 and the driving disc 13 can be changed, thereby controlling the friction torque between the driven disc 12 and the driving disc 13 to achieve the adjustment of the inertia force of the flywheel 1.

[0026] The relationship between the axial force F borne by the piston rod 9 and the pressure of the oil 5 in the upper and lower chambers of the cylinder 7 is as follows:

[0027] F=A c (P2-P1) (1)

[0028] Where A c is the actual effective area of ​​the oil 5, which is the effective cross-sectional area of ​​the piston housing 8 minus the effective cross-sectional area of ​​the piston rod 9, P1 is the oil pressure in the upper chamber of the cylinder 7, and P2 is the oil pressure in the lower chamber of the cylinder 7.

[0029] The relationship between the inlet and outlet oil 5 pressures of the hydraulic motor 4 and the movement of the hydraulic motor 4 is expressed as:

[0030]

[0031] Where T is the output torque of the hydraulic motor 4, D is the ratio of the flow rate of the hydraulic motor 4 to the angular velocity of the output shaft, η m is the mechanical efficiency of the hydraulic motor, P l It is the pressure loss caused by the oil 5 flowing through the hydraulic motor 4.

[0032] In addition, the linear motion of the piston housing 8 and the rotational motion of the output shaft of the hydraulic motor 4 have the following relationship:

[0033]

[0034] Where α is the angular acceleration of the output shaft of the hydraulic motor 4, x is the displacement of the piston housing 8, and η v is the volumetric efficiency of the hydraulic motor 4.

[0035] Since the torque is transmitted between the output shaft of the hydraulic motor 4 and the flywheel 1 through the electromagnetic clutch, the actual output torque of the hydraulic motor 4 has the following relationship with the moment of inertia of the flywheel 1 and the degree of engagement of the electromagnetic clutch:

[0036] T=μIα (4)

[0037] Where μ is the degree of engagement of the electromagnetic clutch, which is controlled by the current and ranges from 0 to 1. When the current is zero, μ = 0, and the force of clutch spring 14 fully engages driven disc 12 and driving disc 13, allowing the torque output by flywheel 1 to act entirely on hydraulic motor 4. When the current reaches the rated current, μ = 1, the electromagnetic clutch is completely disengaged, and no torque is transferred between flywheel 1 and the output shaft of hydraulic motor 4. I is the flywheel's moment of inertia.

[0038] Therefore, the pressure difference of the oil 5 in the upper and lower chambers of the cylinder 7 can be expressed as:

[0039]

[0040] The pressure loss of the hydraulic motor 4 can be approximately considered to be proportional to its flow rate, and the flow rate is linearly related to the speed. Therefore, the pressure loss of the hydraulic motor 4 can be further expressed as:

[0041] P l =Kx (6)

[0042] Where K is the pressure loss coefficient.

[0043] Combining the above equations, we can get:

[0044]

[0045] The inertia coefficient of the device is:

[0046]

[0047] When connected to different external networks, rotating motor 3 can operate in three modes: passive control, energy-feedback control, and active control. When no current flows through rotating motor 3, it operates in generator mode. Using the external network to simulate the structural impedance of the mechanical network, rotating motor 3 achieves passive control. When connected to an energy-feedback loop, rotating motor 3 utilizes the relative motion between its rotor and stator to recover system vibration energy. When a control current is input, the torque output by rotating motor 3 is converted by hydraulic motor 4 into oil pressure 5 that acts on the piston surface, achieving active control.

[0048] The above technical solutions only reflect the preferred technical solutions of the technical solutions of the present invention. Any changes that may be made to certain parts thereof by those skilled in the art all reflect the principles of the present invention and fall within the scope of protection of the present invention.

Claims

1. A multi-mode controllable high-mobility vehicle inertia damping device, characterized in that: The invention comprises an upper lifting ear (6), a cylinder (7) arranged below the upper lifting ear (6), a piston mechanism arranged in the cylinder (7), a lower lifting ear (10) arranged below the piston mechanism, a hydraulic motor (4) arranged outside the cylinder (7), a rotary motor (3), and an electromagnetic clutch arranged above the rotary motor (3); the inner wall of the cylinder (7) is provided with two upper and lower flow channels to connect the oil inlet and oil outlet of the hydraulic motor (4) with the upper chamber and lower chamber of the cylinder (7); the output shaft of the hydraulic motor (4) is connected to the rotor shaft of the rotary motor (3); the driven shaft (11) of the electromagnetic clutch is fixedly connected to the flywheel (1); the piston mechanism passes through the lower end of the cylinder (7) and is fixedly connected to the lower lifting ear (10); and the upper lifting ear (6) is fixedly connected to the upper end of the cylinder (7); The electromagnetic clutch further comprises an electromagnetic clutch housing (2), a driving disc (13) arranged inside the electromagnetic clutch housing (2), and a driven disc (12) arranged above the driving disc (13); the driving disc (13) is fixed inside the electromagnetic clutch housing (2); the driven shaft (11) is arranged on the driven disc (12); a clutch spring (14) is nested outside the driven shaft (11); and a clutch winding (15) is fixed around the inside of the driven disc (12); The rotor shaft of the rotating motor (3) is connected to the electromagnetic clutch housing (2); The piston mechanism comprises a piston housing (8) disposed in a cylinder (7) and a piston rod (9) disposed at the lower end of the piston housing (8); the piston rod (9), the piston and the cylinder (7) are aligned in axis, and the piston and the piston rod (9) have the freedom of linear motion relative to the cylinder (7); The clutch spring (14) in the electromagnetic clutch is initially in a compressed state. When no current flows through the clutch winding (15), the driven disc (12) is in full contact with the driving disc (13) under the thrust of the clutch spring (14). When the rotating motor (3) drives the electromagnetic clutch housing (2) to rotate, the friction torque is transmitted to the driven disc (12) through the driving disc (13), thereby driving the driven shaft (11) and the flywheel (1) to rotate, realizing inertial packaging and outputting inertial force. When current flows through the clutch winding (15), the clutch winding (15) generates electromagnetic force, pushing the driven disc (12) to perform linear motion relative to the driving disc (13). By controlling the current size, the contact pressure between the driven disc (12) and the driving disc (13) can be changed, thereby controlling the friction torque between the driven disc (12) and the driving disc (13) to achieve the adjustment of the flywheel inertia force. When no current flows through the rotating motor (3), it operates in a generator mode, and the rotating motor (3) can utilize an external network to simulate the mechanical network structure impedance, thereby realizing passive control. When the rotating motor (3) is connected to an energy feeding loop, the relative movement between the rotor and the stator of the rotating motor (3) is utilized to recover the system vibration energy. When a control current is input, the torque output by the rotating motor (3) is converted into oil (5) pressure through a hydraulic motor (4) to act on the piston surface, thereby realizing active control.

2. The multi-mode controllable high-mobility vehicle inertia damping device according to claim 1, characterized in that: The piston mechanism further comprises a piston upper cover (16) arranged in the piston housing (8) and a sliding valve assembly arranged in the piston housing (8); the piston upper cover (16) is fixedly mounted on the upper end of the piston housing (8); the sliding valve assembly is fixedly mounted on the lower end of the piston housing (8); a central hole is opened in the piston upper cover (16); the piston rod (9) is fixedly connected to the lower hanging ear (10); and a circular hole is opened between the sliding valve assembly and the piston housing (8); The lower end of the piston upper cover (16) matches the upper end of the slide valve (19) in shape and fits tightly together when the two are covered.

3. The multi-mode controllable high-mobility vehicle inertia damping device according to claim 2, characterized in that: The slide valve assembly comprises a slide valve support (17), a slide valve (19) arranged on the slide valve support (17), a slide valve winding (18) arranged below the slide valve (19), and a slide valve spring (20) arranged below the slide valve (19); the slide valve support (17) is fixedly connected to the lower end of the piston housing (8); a circular hole is provided between the slide valve support (17) and the piston housing (8); the slide valve winding (18) is fixedly surrounded inside the slide valve support (17); one end of the slide valve spring (20) is fixedly connected to the slide valve (19), and the other end thereof is fixedly connected to the slide valve support (17); The axes of the slide valve (19) and the slide valve support (17) are aligned, and the slide valve (19) and the slide valve support (17) have the freedom of relative linear movement.

4. The multi-mode controllable high-mobility vehicle inertia damping device according to claim 1, characterized in that: The clutch spring (14) is aligned with the axis of the driven shaft (11); the driven shaft (11) has a degree of freedom of rotational motion relative to the electromagnetic clutch housing (2); and the driven shaft (11) has a degree of freedom of linear motion relative to the driven disc (12).

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