A series-parallel switching inertia damping device

Abstract

The present invention discloses a series-parallel switching inertia capacity damping device, comprising an upper lifting ear, an outer cylinder arranged below the upper lifting ear, a spiral tube arranged on the outer cylinder, an inertia capacity piston arranged in the outer cylinder, an inner cylinder arranged in the outer cylinder and connected to the inertia capacity piston, a damping piston arranged in the inner cylinder, a piston rod arranged on the damping piston, a lower lifting ear arranged below the piston rod, a stator winding arranged at the lower end of the outer cylinder, and a rotor magnet arranged on the outer side of the inner cylinder. The upper lifting ear is fixedly connected to the outer cylinder, the spiral tube is connected to the inside of the outer cylinder, the inertia capacity piston is fixedly connected to the inner cylinder, the upper end of the inner cylinder is opened, a slender damping hole is opened on the damping piston, the damping piston is fixedly connected to the piston rod, the stator winding and the rotor magnet are coaxially and tightly fitted, and the piston rod is fixedly connected to the lower lifting ear. The beneficial effect is that the inertia capacity damping can be switched between a series structure and a parallel structure, thereby improving the vibration isolation performance of the device; at the same time, the present invention has the characteristics of simple structure and small size.

Description

Technical Field

[0001] The invention relates to the technical field of vehicle suspension, in particular to a series-parallel switching inertia-capacitance damping device. Background Art

[0002] As a key component of the automotive chassis system, the suspension significantly impacts the vehicle's handling stability, ride comfort, and driving safety. With the emergence of inertia capacitors as dual-point mass elements, they have garnered widespread attention in the field of engineering vibration isolation. Research has found that inertia capacitors and dampers exhibit varying performance in different configurations, and that combining them in a series-parallel configuration can effectively improve vehicle suspension vibration isolation performance. However, limited chassis space precludes the effective application of multi-element inertia capacitor-damping structures. Furthermore, varying road conditions necessitate varying vibration isolation performance requirements, necessitating the dynamic selection and switching between series and parallel configurations.

[0003] In view of the above situation, it is necessary to improve the existing inertia damping device so that it can adapt to the current demand for vehicle suspension vibration isolation performance. Summary of the Invention

[0004] The purpose of the present invention is to solve the problems of structural integrated design and series-parallel switching of an inertia capacitance damping device.

[0005] The technical solution of the present invention for achieving the above-mentioned purpose is a series-parallel switching inertia damping device, comprising an upper lifting ear, an outer cylinder arranged below the upper lifting ear, a spiral tube arranged on the outer cylinder, an inertia piston arranged in the outer cylinder, an inner cylinder arranged in the outer cylinder and connected to the inertia piston, a damping piston arranged in the inner cylinder, a piston rod arranged on the damping piston, a lower lifting ear arranged below the piston rod, a stator winding arranged at the lower end of the outer cylinder, and a rotor magnet arranged on the outside of the inner cylinder, the upper lifting ear is fixedly connected to the outer cylinder, the spiral tube is communicated with the inside of the outer cylinder, the inertia piston is fixedly connected to the inner cylinder, the upper end of the inner cylinder is opened, a slender damping hole is opened on the damping piston, the damping piston is fixedly connected to the piston rod, the stator winding and the rotor magnet are coaxially and tightly fitted, and the piston rod is fixedly connected to the lower lifting ear.

[0006] As a further supplement to the technical solution, the inertial piston is axially matched with the hole on the inner wall of the outer cylinder.

[0007] As a further supplement to the technical solution, the inner tube is axially matched with the hole at the lower end of the outer tube, and the upper end of the inner tube passes through the inertial piston and protrudes from the surface of the inertial piston.

[0008] As a further supplement to the technical solution, the inertial piston and the inner cylinder have the freedom to move linearly along the axis within the outer cylinder.

[0009] As a further supplement to the technical solution, the damping piston is axially matched with the hole on the inner wall of the inner cylinder.

[0010] As a further supplement to the technical solution, the damping piston and the piston rod have the freedom to move linearly along the axis of the inner cylinder.

[0011] As a further supplement to the present technical solution, the stator winding and the rotor magnet have the freedom to move vertically along the axis.

[0012] Its beneficial effect is that the present invention proposes a series-parallel switching inertia-capacitive damping device. According to different working conditions, when there is no current input to the outer cylinder stator winding, the inner cylinder and the outer cylinder can move relative to each other. When the damping piston pushes the oil to generate a damping force, the oil volume balance between the inner and outer cylinders is utilized to make the inertia-capacitive piston on the inner cylinder push the oil to flow along the spiral tube, thereby realizing the series output characteristic of the inertia force and the damping force; when the outer cylinder stator winding inputs current, the inner cylinder and the outer cylinder are relatively stationary. When the damping piston pushes the oil to generate a damping force, the oil between the inner and outer cylinders is connected and flows through the spiral tube, thereby realizing the parallel output characteristic of the inertia force and the damping force; therefore, by controlling the outer cylinder winding to generate electromagnetic force, the inertia-capacitive damping can be switched between the series structure and the parallel structure, thereby improving the vibration isolation performance of the device; at the same time, the present invention has the characteristics of simple structure and small size, which is conducive to the installation application in the vehicle chassis space. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a front view of the structure of the present invention;

[0014] Figure 2 It is a cross-sectional view of the structure of the present invention;

[0015] Figure 3 It is a schematic diagram of the oil flow direction when the piston rod performs the push motion under the series structure of the present invention;

[0016] Figure 4 Schematic diagram of the oil flow direction when the piston rod performs return motion under the series structure of the present invention;

[0017] Figure 5 It is a schematic diagram of the oil flow direction when the piston rod performs the push motion under the parallel structure of the present invention;

[0018] Figure 6 Schematic diagram of the oil flow direction when the piston rod performs return motion under the parallel structure of the present invention;

[0019] In the figure, 1, upper lifting ear; 2, outer cylinder; 3, spiral tube; 4, inertia piston; 5, inner cylinder; 6, damping piston; 7, piston rod; 8, lower lifting ear; 9, stator winding; 10, rotor magnet. DETAILED DESCRIPTION

[0020] In order to make the technical solution more clear to those skilled in the art, Figure 1-6 The technical solution of the present invention is described in detail:

[0021] like Figure 1-2 As shown, a series-parallel switching inertia damping device includes an upper lifting ear 1, an outer tube 2 arranged below the upper lifting ear 1, a spiral tube 3 arranged on the outer tube 2, an inertia piston 4 arranged in the outer tube 2, an inner tube 5 arranged in the outer tube 2 and connected to the inertia piston 4, a damping piston 6 arranged in the inner tube 5, a piston rod 7 arranged on the damping piston 6, a lower lifting ear 8 arranged below the piston rod 7, a stator winding 9 arranged at the lower end of the outer tube 2, and a rotor magnet 10 arranged outside the inner tube 5. The upper lifting ear 1 is fixedly connected to the outer tube 2 to form an end point of the device; the spiral tube 3 is connected to the inside of the outer tube 2, wherein the inertia piston 4 is axially matched with the inner wall hole of the outer tube 2; the inertia piston 4 is axially matched with the inner wall hole of the inner tube 2; The cylinder 5 is fixedly connected, and a hole is opened at the upper end of the inner cylinder 5 so that the oil in the inner cylinder 5 is connected to the oil in the outer cylinder 2. A slender damping hole is opened on the damping piston 6, and the damping piston 6 is fixedly connected to the piston rod 7. The stator winding 9 and the rotor magnet 10 are coaxially and tightly fitted, and the two have the freedom to move vertically along the axis; the piston rod 7 is fixedly connected to the lower ear 8; the inner cylinder 5 is matched with the hole axis at the lower end of the outer cylinder 2, and the upper end of the inner cylinder 5 passes through the inertial piston 4 and protrudes from the surface of the inertial piston 4; the inertial piston 4 and the inner cylinder 5 have the freedom to move linearly along the axis in the outer cylinder 2; the damping piston 6 is matched with the hole axis on the inner wall of the inner cylinder 5; the damping piston 6 and the piston rod 7 have the freedom to move linearly along the axis of the inner cylinder 5.

[0022] When no current flows through the stator winding 9—that is, when the device is in a series configuration—during specific implementation, when relative motion occurs between the fixed endpoints of the upper and lower lifting lugs 1 and 8, the lower lifting lug 8, connected to the piston rod 7, pushes the damping piston 6 and inner tube 5 to generate relative linear motion. The oil in the upper and lower chambers of the inner tube 5 generates a damping force through the elongated damping orifice in the damping piston 6. Simultaneously, due to the volume of the piston rod 7, the volume of the oil in the upper and lower chambers of the inner tube 5 changes inconsistently, resulting in flow compensation between the oil in the outer tube 2 and the inner tube 5. This causes a volume change in the upper chamber of the outer tube 2, pushing the inertia piston 4 and inner tube 5 to generate linear motion relative to the outer tube 2, thereby pushing the oil in the outer tube 2 through the spiral tube 3, generating an inertial force through the oil flow. Simultaneously, during the relative motion between the inner tube 5 and the outer tube 2, the stator winding 9 and the rotor magnet 10 operate in a feedback state, enabling vibration energy recovery.

[0023] like Figure 3As shown, when the two end points of the device are relatively compressed, the lower lifting ear 8 connected to the piston rod 7 makes a linear motion, and the oil in the inner cylinder 5 flows from the upper chamber to the lower chamber through the damping hole. At the same time, due to the increase in the volume occupied by the piston rod 7 in the inner chamber, part of the oil in the upper chamber of the inner cylinder 5 flows to the upper chamber of the outer cylinder 2, so that the volume of the oil in the upper chamber of the outer cylinder 2 increases, pushing the inertial piston 4 and the inner cylinder 5 to stretch relative to the outer cylinder 2, and at the same time pushing the oil in the lower chamber of the outer cylinder 2 to flow into the spiral tube 3, and the oil flows along the spiral tube 3 to the upper chamber of the outer cylinder 2.

[0024] like Figure 4 As shown, when the two end points of the device are relatively stretched, the lower lifting ear 8 connected to the piston rod 7 makes a linear motion, and the oil in the inner cylinder 5 flows from the lower chamber to the upper chamber through the damping hole. At the same time, since the volume occupied by the piston rod 7 in the inner chamber is reduced, part of the oil in the upper chamber of the outer cylinder 2 flows to the upper chamber of the inner cylinder 5, so that the volume of the oil in the upper chamber of the outer cylinder 2 is reduced, pushing the inertial piston 4 and the inner cylinder 5 to generate a compression movement relative to the outer cylinder 2, and at the same time pushing the oil in the upper chamber of the outer cylinder 2 to flow into the spiral tube 3, and the oil flows along the spiral tube 3 to the lower chamber of the outer cylinder 2.

[0025] When an external current flows through stator winding 9, meaning the device is in a parallel configuration, outer cylinder 2 and inner cylinder 5 are in a relatively static state. When relative motion occurs between the fixed endpoints of upper and lower lugs 1 and 8, lower lug 8 connects to piston rod 7, pushing damping piston 6 and inner cylinder 5 to produce relative linear motion. The oil in the upper and lower chambers of inner cylinder 5 generates a damping force through the elongated damping orifice in damping piston 6. Simultaneously, due to the volume of piston rod 7, the volume of the oil in the upper and lower chambers of inner cylinder 5 changes inconsistently, resulting in flow compensation between the oil in outer cylinder 2 and the oil in inner cylinder 5. This causes a change in the volume of the oil in the upper chamber of outer cylinder 2. The oil in outer cylinder 2 passes through spiral tube 3, generating an inertial force through the flow of the oil. During this process, the inner and outer cylinders are fixed, and the oil flow achieves a parallel output of inertial and damping forces, realizing the characteristics of a parallel inertial capacitance damping structure.

[0026] The damping coefficient c of the device is

[0027]

[0028] Where S3 is the cross-sectional area of ​​the damping hole in the damping piston, μ is the dynamic viscosity of the oil, d is the diameter of the damping hole, l d is the length of the damping hole, and n is the number of damping holes.

[0029] The inertia coefficient b of the device is

[0030]

[0031] Wherein, m is the mass of oil in the spiral tube 3, r4 is the spiral radius of the spiral tube 3, h is the lead of the spiral tube 3, S1 is the cross-sectional area of ​​the inertial piston 4, S2 is the cross-sectional area of ​​the spiral tube 3, and S5 is the cross-sectional area of ​​the piston rod 7.

[0032] like Figure 5 As shown, when the two end points of the device are relatively compressed, the lower lifting ear 8 connected to the piston rod 7 makes a linear motion, and the oil in the inner cylinder 5 flows from the upper chamber to the lower chamber through the damping hole. At the same time, due to the increase in the volume occupied by the piston rod 7 in the inner chamber, part of the oil in the upper chamber of the inner cylinder 5 flows to the upper chamber of the outer cylinder 2, so that the volume of the oil in the upper chamber of the outer cylinder 2 increases, pushing the oil in the upper chamber of the outer cylinder 2 to flow along the spiral tube 3 to the lower chamber of the outer cylinder 2.

[0033] like Figure 6 As shown, when the two end points of the device are relatively stretched, the lower lifting ear 8 connected to the piston rod 7 makes a linear motion, and the oil in the inner cylinder 5 flows from the lower chamber to the upper chamber through the damping hole. At the same time, since the volume occupied by the piston rod 7 in the inner chamber is reduced, part of the oil in the upper chamber of the outer cylinder 2 flows to the upper chamber of the inner cylinder 5, so that the volume of the oil in the upper chamber of the outer cylinder 2 is reduced, and the oil is pushed into the upper chamber of the outer cylinder 2 through the spiral tube 3.

[0034] During the specific implementation process, the inertia piston 4 and the inner cylinder 5 move freely in a straight line relative to the outer cylinder 2 and the damping piston 6. The movement stroke is not affected by the linear movement of the upper lifting ear 1 and the lower lifting ear 8 of the device. The series or parallel output of the inertia force and the damping force is achieved through the balance of oil volume. The structural design of the series switching of the inertia capacity and damping is realized by controlling the stator winding 9 and the rotor magnet 10 through an external power supply.

[0035] By analyzing the working principle of the device, we can know that:

[0036] This device uses a slender damping hole, and the flow formula is:

[0037]

[0038] Where: Q is the flow rate of the damping hole, μ is the dynamic or absolute viscosity of the oil, Δp is the pressure difference between the upper and lower parts of the damping valve, l d is the length of the damping hole, d is the diameter of the damping hole, and n is the number of damping holes.

[0039] When the damping piston 6 produces linear motion relative to the inner cylinder 5, the oil flow rate of the damping hole is:

[0040] Q=S3x1 (4)

[0041] Wherein S3 is the cross-sectional area of ​​the damping piston 6 , and x1 is the displacement of the damping piston 6 relative to the inner cylinder 5 .

[0042] Multiplying the left and right sides of formula (3) by the effective area S3 of the small piston yields:

[0043]

[0044] The damping force F generated by the damping hole is calculated c for:

[0045]

[0046] The damping coefficient c of the device is

[0047]

[0048] Affected by the volume of the piston rod 7, the oil compensation volume V between the upper chamber of the inner tube 5 and the upper chamber of the outer tube 2 is:

[0049] V=S5x1 (8)

[0050] Wherein S5 is the cross-sectional area of ​​the piston rod 7.

[0051] Therefore, the displacement x2 of the inertial piston 4 relative to the outer cylinder 2 caused by the oil compensation is

[0052]

[0053] Where S1 is the cross-sectional area of ​​the inertial piston 4.

[0054] The length of spiral tube 3 is

[0055] l=z2πr4 (10)

[0056] Where z is the number of turns of helical tube 3, and r4 is the helical radius of helical tube 3.

[0057] Therefore, the mass of the oil in the spiral tube 3 is

[0058] m=ρS2l (11)

[0059] Where S2 is the cross-sectional area of ​​the spiral tube 3, and ρ is the density of the oil.

[0060] The moment of inertia of the oil in the spiral tube 3 is:

[0061] J=mr4 2 (12)

[0062] Due to the conservation of oil volume, when the inertial piston 4 is displaced relative to the outer cylinder 2, the volume of oil in the spiral tube 3 changes as follows:

[0063]

[0064] Where h is the pitch of the external spiral tube 3, and θ is the corresponding turning angle when the fluid enters the spiral tube 3.

[0065] According to the law of conservation of energy, we can get

[0066]

[0067] Substituting formula (9) into the above formula, the series inertia coefficient of the device can be obtained as follows:

[0068]

[0069] 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 series-parallel switching inertia damping device, characterized in that: The invention comprises an upper lifting ear (1), an outer cylinder (2) arranged below the upper lifting ear (1), a spiral tube (3) arranged on the outer cylinder (2), an inertial piston (4) arranged in the outer cylinder (2), an inner cylinder (5) arranged in the outer cylinder (2) and connected to the inertial piston (4), a damping piston (6) arranged in the inner cylinder (5), a piston rod (7) arranged on the damping piston (6), a lower lifting ear (8) arranged below the piston rod (7), a stator winding (9) arranged at the lower end of the outer cylinder (2), and a rotor magnet (10) arranged outside the inner cylinder (5); the upper lifting ear (1) is fixedly connected to the outer cylinder (2); the spiral tube (3) is fixedly connected to the inner cylinder (2); and the inner cylinder (5) is fixedly connected to the outer cylinder (2). The inner cylinder (5) and the outer cylinder (2) are connected to each other, and the fluid ports of the spiral tube (3) are respectively arranged on the upper side and the lower side of the inertial piston (4). The inertial piston (4) is fixedly connected to the inner cylinder (5). The upper end of the inner cylinder (5) is opened so that the oil in the inner cylinder (5) is connected to the oil in the outer cylinder (2); the damping piston (6) is provided with a slender damping hole that can realize two-way circulation. The damping piston (6) is fixedly connected to the piston rod (7). The damping piston (6) and the piston rod (7) have the freedom of linear motion along the axis of the inner cylinder (5); the stator winding (9) and the rotor magnet (10) are coaxially and tightly fitted, and the piston rod (7) is fixedly connected to the lower hanging ear (8); When no current is input to the outer cylinder stator winding (9), the inner cylinder (5) and the outer cylinder (2) can move relative to each other. When the damping piston (6) pushes the oil to generate a damping force, the inertia piston (4) on the inner cylinder (5) pushes the oil to flow along the spiral tube (3) by utilizing the volume balance of the oil between the inner and outer cylinders, thereby realizing the series output characteristic of the inertia force and the damping force. When current is input to the outer cylinder stator winding (9), the inner cylinder (5) and the outer cylinder (2) are relatively stationary. When the damping piston (6) pushes the oil to generate a damping force, the oil between the inner and outer cylinders is connected and flows through the spiral tube (3), thereby realizing the parallel output characteristic of the inertia force and the damping force.

2. The series-parallel switching inertia damping device according to claim 1, characterized in that: The inertial piston (4) is axially matched with the inner wall hole of the outer cylinder (2).

3. The series-parallel switching inertia damping device according to claim 1, characterized in that: The inner cylinder (5) is axially matched with the hole at the lower end of the outer cylinder (2); the upper end of the inner cylinder (5) passes through the inertial piston (4) and protrudes from the surface of the inertial piston (4).

4. The series-parallel switching inertia damping device according to claim 1, characterized in that: The damping piston (6) is axially matched with the inner wall hole of the inner cylinder (5).

5. The series-parallel switching inertia damping device according to claim 1, characterized in that: The stator winding (9) and the rotor magnet (10) have the freedom to move linearly along the axis.

Images