A special vehicle adaptive fluid inertia container

Abstract

The present invention discloses an adaptive fluid inertia container for special vehicles. By means of the stepped structure of the hydraulic cylinder, the connection and separation between the sleeve and the piston, the synchronous movement of the spiral pipe and the spring, and the coordination of the control system, the effective cross-sectional area of the hydraulic cylinder piston, the pitch of the spiral pipe, and the spiral radius of the spiral pipe in the fluid inertia container can be continuously adjusted at any time according to the current vehicle driving conditions, thereby achieving adaptive adjustment of the inertia coefficient of the fluid inertia container.

Description

Technical Field

[0001] The present invention relates to a self-adaptive fluid inertia container for special vehicles, which is a self-adaptive fluid inertia container whose inertia value can be continuously adjusted according to working conditions, does not require manual control and is easy to manufacture. Background Art

[0002] With the continuous advancement of China's urbanization process, the demand for special-purpose vehicles is growing rapidly, and the domestic market has huge potential. As a means of transportation with large load variations, the suspension system of special-purpose vehicles has a very significant impact on the operating accuracy and road damage of special-purpose vehicles. Existing special-purpose vehicle suspension systems mostly use a structure of leaf springs and cylinder shock absorbers. However, leaf springs and passive shock absorbers have the disadvantages of unadjustable stiffness and uncontrollable damping, which seriously affects the ride comfort, handling stability, and road friendliness of special-purpose vehicles. Especially during operations, such as dredging, loading and unloading garbage, and vacuuming sewage, the dynamic performance of the chassis suspension system seriously restricts the operating accuracy, safety and stability of special-purpose vehicles.

[0003] Existing dedicated automotive suspensions are based on a traditional "spring-damper" structure. The lack of mass impedance has led to a performance bottleneck. In 2003, Cambridge University scholar Smith, based on electromechanical similarity theory, creatively proposed an ideal element, the inertia capacitor, that is ground-free and completely analogous to a capacitor. He also demonstrated a physical implementation and began research on its application in vehicle suspension systems, exploring a new approach to improving suspension performance. The emergence and application of inertia capacitors has significantly improved vehicle vibration damping performance.

[0004] After years of research and innovation, most existing inertia chambers have fixed inertia coefficients. These can only be used in passive vehicle suspensions, are unable to actively adjust their inertia coefficients based on road conditions, and lack good road adaptability.

[0005] Although variable inertia coefficient inertia vessels have been designed, they have disadvantages such as difficult processing, control time lag, and the inability to continuously change the inertia coefficient.

[0006] Patent application number CN202110206185.1, titled "A Reciprocating Screw Inertia Device with Adjustable Inertia Coefficient," utilizes a crescent pin to switch between two grooves in the screw's lead to achieve adjustable inertia coefficient. However, this invention cannot achieve continuous adjustment of the inertia coefficient at any time, requiring switching at a fixed position, limiting its practical engineering value.

[0007] Patent application number 201420698814.2, titled "Two-stage adjustable inertia chamber," utilizes electromagnetic phenomena to alter the distribution of magnets within a flywheel, thereby changing the flywheel's moment of inertia. However, achieving this external current change still requires the installation of other devices for real-time control, making implementation complex and limiting its practical engineering value.

[0008] Therefore, how to design an inertia container device that does not require control, is simple and feasible, easy to manufacture, and whose inertia value can be adjusted at any time according to working conditions, to alleviate the instantaneous impact caused by the immutable inertia value when a large load acts instantly, has become a difficult problem that needs to be solved urgently. Summary of the Invention

[0009] Based on research into the limited engineering utility of existing adjustable inertia chambers and the associated mechanical structures, this invention utilizes a stepped design of the hydraulic cylinder, the connection and separation of the sleeve and piston, the synchronized movement of the spiral conduit and spring, and a coordinated control system to achieve continuous, on-the-fly adjustment of the effective cross-sectional area of the hydraulic cylinder piston, the pitch of the spiral conduit, and the spiral radius of the spiral conduit within the fluid inertia chamber, thereby enabling adaptive adjustment of the fluid inertia chamber's inertia coefficient. Furthermore, the invention encapsulates the entire device and incorporates sealing rings in selected locations, facilitating installation and extending its service life.

[0010] In order to achieve the above-mentioned object, the present invention adopts the following technical solution: a special vehicle adaptive fluid inertia container, comprising a pipe port (3), a hydraulic cylinder (4), a connecting rod (8), a piston (9), a bottom plate (11), a guide spring (13), a spiral pipe (15), and an inertia container cylinder (16);

[0011] The upper end of the inertial cylinder (16) is provided with a through hole, in which a connecting rod (8) is accommodated, a piston (9) is fixed on the connecting rod (8), and the connecting rod (8) extends upward from the through hole; the hydraulic cylinder (4) is fixedly connected to the upper part of the inertial cylinder (16); the upper end of the hydraulic cylinder (4) is also provided with a through hole, in which a connecting rod (8) is accommodated, and the connecting rod (8) extends upward from the through hole; the lower end of the hydraulic cylinder (4) is also provided with a through hole, in which a connecting rod (8) is accommodated, and the connecting rod (8) extends downward from the through hole; the lower end of the connecting rod (8) is fixedly connected to the bottom plate (11);

[0012] The hydraulic cylinder (4) is designed in a stepped manner and is divided into a first hydraulic chamber (4-1) and a second hydraulic chamber (4-2). An upper pipe opening (3-1) is provided at the upper end of the first hydraulic chamber (4-1), and a lower pipe opening (3-2) is provided at the lower end of the second hydraulic chamber (4-2). The upper pipe opening (3-1) and the lower pipe opening (3-2) are connected via a spiral pipe (15).

[0013] The guide spring (13) is arranged along the outer periphery of the hydraulic cylinder (4) and is divided into a first guide spring portion (13-1) and a second guide spring portion (13-2). The upper end of the guide spring (13) is fixed to the lower end inside the inertia cylinder (16), and the lower end is fixed to the bottom plate (11). The outer end of the first guide spring portion (13-1) is wound with a spiral pipe (15).

[0014] Furthermore, the sleeve (5) is slidably mounted on the inner wall of the first hydraulic chamber (4-1), and a connecting key (6) and a control box (7) are fixedly mounted in the sleeve (5);

[0015] The control box (7) is equipped with a control system and a sensor. The control system controls the state of the connection key (6) according to the signal collected by the sensor: "pop out" and "retract".

[0016] The sensor is installed at the bottom of the sleeve (5) and mainly monitors whether the bottom of the sleeve (5) contacts the stepped portion of the hydraulic cylinder (4); if the bottom of the sleeve (5) contacts the stepped portion of the hydraulic cylinder (4), the control system controls the state of the connection key to be "retracted"; if the bottom of the sleeve (5) is separated from the stepped portion of the hydraulic cylinder (4), the control system controls the state of the connection key to be "ejected".

[0017] Furthermore, the first hydraulic chamber (4-1) is located above the second hydraulic chamber (4-2), and the volume of the first hydraulic chamber (4-1) is larger than that of the second hydraulic chamber (4-2).

[0018] Furthermore, the cross section of the piston (9) is in the shape of an I, comprising a small diameter portion (9-1) and a large diameter portion (9-2); the outer diameter of the large diameter portion (9-2) is the same as the inner diameter of the second hydraulic chamber (4-2), and the outer diameter of the large diameter portion (9-2) is larger than the minimum inner diameter of the sleeve (5); the outer diameter of the small diameter portion (9-1) is smaller than the inner diameter of the second hydraulic chamber (4-2), and a groove is formed between the small diameter portion (9-1) and the large diameter portion (9-2).

[0019] Furthermore, the lower end of the inertia cylinder (16) is fixedly connected to a lower lifting lug (12), and the lower lifting lug (12) is fixedly connected to the lower end point of the vibration isolation system; the upper end of the connecting rod (8) is fixedly connected (for example, welded) to an upper lifting lug (1), and the upper lifting lug (1) is fixedly connected to the upper end point of the vibration isolation system.

[0020] Furthermore, an upper buffer spring (2) is provided inside the upper portion of the hydraulic cylinder (4) to alleviate the impact of the sleeve (5) and the piston (9) on the hydraulic cylinder (4) when they move upward; and a lower buffer spring (10) is provided inside the lower portion of the hydraulic cylinder (4) to alleviate the impact of the piston (9) on the hydraulic cylinder (4) when it moves downward.

[0021] Furthermore, when the inertia container is in operation, a sealing ring I (14) is installed at the outer end of the sleeve (5).

[0022] Furthermore, a sealing ring II (17) is installed at the connection between the inertia cylinder (3), the hydraulic cylinder (4) and the connecting rod (8).

[0023] The beneficial effects of adopting the above technical solution are:

[0024] 1. The design of a stepped hydraulic cylinder and a "connectable and disconnectable sleeve and piston" changes the effective cross-sectional area of the hydraulic cylinder piston, thereby changing the inertia coefficient of the inertia chamber. This solves the problem of "unchangeable effective cross-sectional area of the piston" in fluid inertia chambers.

[0025] 2. The design of "guide spring drives the spiral pipe to move" is adopted. The spiral pipe is wrapped around part of the guide spring. When the guide spring is stretched or compressed, the spiral pipe moves with it, thereby changing the pitch and spiral radius of the spiral pipe, and thus changing the inertia coefficient of the inertia container.

[0026] 3. Use "structural connection" and "control connection" to realize the connection and separation of sleeve and piston.

[0027] "Structural connection" refers to the specific design of bosses and grooves on the sleeve and piston surfaces. This design has three main advantages:

[0028] (a) It can realize the connection when the sleeve and piston move upward together;

[0029] (b) It can serve as a "control connection" signal. When the sleeve contacts two specific surfaces of the piston, achieving "structural connection," the bottom of the sleeve separates from the stepped portion of the hydraulic cylinder. A sensor in the control box detects this change in contact between the sleeve and the hydraulic cylinder, transmitting a signal to the control system, "triggering" the control system's control of the connection key.

[0030] (c) It can ensure that the sleeve and the piston are fully connected, that is, the upper end surfaces of the sleeve and the piston are aligned after the connection is completed.

[0031] "Control connection" means changing the connection key status through control systems, sensors, and other electrical equipment. This design has two main advantages:

[0032] (a) It can ensure the connection between the sleeve and the piston when they move upward and downward together;

[0033] (b) “Control connection” has better connection performance and is more stable than “structural connection”.

[0034] 4. The "buffer spring" design mitigates the impact of the sleeve on the hydraulic cylinder during upward and downward movement. This increases the service life of the inertia container and helps to attenuate the impact of the suspension on the road, improving the vehicle's ride smoothness.

[0035] 5. This device requires no external equipment, has a small number of components, and is less prone to failure. It also uses a control system, making it a new type of inertial container device with excellent performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The present invention will be further described below with reference to the accompanying drawings and examples.

[0037] Figure 1 This is a structural schematic diagram of an adaptive fluid inertia container for a special vehicle according to the present invention.

[0038] Figure 2 This is a structural diagram of the present invention in working state 1.

[0039] Figure 3 Schematic diagram of the structure of the present invention in working state 3.

[0040] Figure 4 Schematic diagram of the structure of the present invention in working state 4.

[0041] Figure 5 This is a force analysis diagram of the adaptive fluid inertia container for the special vehicle of the present invention.

[0042] Figure 6 The law of change of the inertia coefficient of the inertia container with the movement of the piston when the effective cross-sectional area of the hydraulic cylinder piston is the largest.

[0043] Figure 7 This is the law of change of the inertia coefficient of the inertia container with the movement of the piston when the effective cross-sectional area of the hydraulic cylinder piston is the smallest.

[0044] Description of reference numerals:

[0045] 1-upper lifting ear, 2-upper buffer spring, 3-pipe port, 3-1 upper pipe port, 3-2 lower pipe port, 4-hydraulic cylinder, 4-1-first hydraulic chamber, 4-2 second hydraulic chamber, 5-sleeve, 5-A-sleeve plane, 6-connecting key, 7-control box, 8-connecting rod, 9-piston, 9-1-small diameter part, 9-2-large diameter part, 9-B-piston plane, 10-lower buffer spring, 11-base plate, 12-lower lifting ear, 13-guide spring, 13-1 first guide spring part, 13-2 second guide spring part, 14-sealing ring I, 15-spiral pipe, 16-inertia cylinder, 17-sealing ring II. DETAILED DESCRIPTION

[0046] The present invention will be further described below with reference to the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereto.

[0047] In the description of the present invention, it should be noted that the terms "upper," "lower," "inner," "outer," "front end," "rear end," "both ends," "one end," "the other end," and the like, indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely to facilitate and simplify the description of the present invention. They are not intended to indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0048] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "installed," "provided with," "connected," etc., should be understood in a broad sense. For example, "connected" may refer to a fixed connection, a detachable connection, or an integral connection; it may refer to a mechanical connection or an electrical connection; it may refer to a direct connection or an indirect connection through an intermediate medium; it may refer to internal communication between two components. Those skilled in the art will be able to understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0049] The core concept of the present invention is to achieve continuous adjustment of the effective cross-sectional area of the hydraulic cylinder piston, the pitch of the spiral pipe, and the spiral radius of the spiral pipe in the fluid inertia container at any time through the stepped design of the hydraulic cylinder, the connection and separation of the sleeve and piston, the synchronous movement of the spiral pipe and the spring, and the coordination of the control system, thereby realizing adaptive adjustment of the inertia coefficient of the fluid inertia container.

[0050] The adaptive fluid inertia container for special vehicles proposed in this invention primarily comprises an upper lifting lug 1, an upper buffer spring 2, a pipe opening 3, a hydraulic cylinder 4, a sleeve 5, a connecting key 6, a control box 7, a connecting rod 8, a piston 9, a lower buffer spring 10, a base plate 11, a lower lifting lug 12, a guide spring 13, a sealing ring I 14, a spiral pipe 15, an inertia container 16, and a sealing ring II 17. The pipe opening 3 is divided into an upper pipe opening 3-1 and a lower pipe opening 3-2 based on its position; the hydraulic cylinder 4 is divided into a first hydraulic chamber 4-1 and a second hydraulic chamber 4-2 based on its cross-sectional area; and the guide spring 13 is divided into a first guide spring portion 13-1 and a second guide spring portion 13-2 based on whether the spiral pipe is wound around it.

[0051] Among them, Figure 1As shown, a through hole is formed at the upper end of the inertia cylinder 16, in which a connecting rod 8 is housed, extending upward from the through hole. A lower lifting lug 12 is fixedly connected to the lower end of the vibration isolation system. An upper lifting lug 1 is fixedly connected (e.g., welded) to the upper end of the connecting rod 8, which is fixedly connected to the upper end of the vibration isolation system. The hydraulic cylinder 4 is fixedly connected (e.g., welded) to the upper interior of the inertia cylinder 16. The hydraulic cylinder 4 has a stepped design and is divided into a first hydraulic chamber 4-1 and a second hydraulic chamber 4-2. The first hydraulic chamber 4-1 is located above the second hydraulic chamber 4-2, and the volume of the first hydraulic chamber 4-1 is larger than that of the second hydraulic chamber 4-2. A through hole is also provided at the upper end of the hydraulic cylinder 4, in which a connecting rod 8 is accommodated, and the connecting rod 8 extends upward from the through hole; a through hole is also provided at the lower end of the hydraulic cylinder 4, in which a connecting rod 8 is accommodated, and the connecting rod 8 extends downward from the through hole, and the lower end of the connecting rod 8 is fixedly connected (for example, welded) to a base plate 11.

[0052] An upper conduit opening 3-1 is defined at the upper end of the first hydraulic chamber 4-1, and a lower conduit opening 3-2 is defined at the lower end of the second hydraulic chamber 4-2. The upper and lower conduit openings 3-1 and 3-2 are connected by a spiral conduit 15. A guide spring 13 is arranged along the outer circumference of the hydraulic cylinder 4, with its upper end fixed (e.g., welded) to the lower end of the inertia cylinder 16 and its lower end fixed (e.g., welded) to the base plate 11. The spiral conduit 15 is wrapped around the outer end of the first guide spring portion 13-1 (e.g., secured by a clip).

[0053] Among them, the sleeve 5 is slidably installed on the inner wall of the first hydraulic chamber 4-1, and the sleeve 5 is fixedly installed with a connecting key 6 and a control box 7. The control box 7 is equipped with a control system and a sensor. The control system controls the state of the connecting key 6: "pop out" and "retract" according to the signal collected by the sensor. Among them, the sensor is installed at the bottom of the sleeve 5, mainly monitoring whether the bottom of the sleeve 5 is in contact with the stepped part of the hydraulic cylinder 4. If the bottom of the sleeve 5 is in contact with the stepped part of the hydraulic cylinder 4, the control system controls the state of the connecting key to "retract"; if the bottom of the sleeve 5 is separated from the stepped part of the hydraulic cylinder 4, the control system controls the state of the connecting key to "pop out".

[0054] A piston 9 is fixed to the connecting rod 8. The piston 9 has an I-shaped cross-section, consisting of a small-diameter portion 9-1 and a large-diameter portion 9-2. The outer diameter of the large-diameter portion 9-2 is the same as the inner diameter of the second hydraulic chamber 4-2. The outer diameter of the large-diameter portion 9-2 is larger than the minimum inner diameter of the sleeve 5, while the outer diameter of the small-diameter portion 9-1 is smaller than the inner diameter of the second hydraulic chamber 4-2. A groove is formed between the small-diameter portion 9-1 and the large-diameter portion 9-2.

[0055] An upper buffer spring 2 is also provided above the inside of the hydraulic cylinder 4 to relieve the impact of the sleeve 5 and the piston 9 on the hydraulic cylinder 4 when they move upward. A lower buffer spring 10 is also provided below the inside of the hydraulic cylinder 4 to relieve the impact of the piston 9 on the hydraulic cylinder 4 when they move downward.

[0056] When the inertia container is working, in order to prevent the oil from flowing through the gap between the sleeve 5 and the hydraulic cylinder 4 and affecting the inertia performance of the inertia container, a sealing ring I14 is installed on the outer end of the sleeve 5.

[0057] In order to improve the sealing performance of the inertial container and prevent the intrusion of external dust, a sealing ring II 17 is installed at the connection between the inertial container barrel 3, the hydraulic cylinder barrel 4 and the connecting rod 8.

[0058] like Figure 2 As shown, the device is in working state 1. At this time, the state of the connecting key is "ejected". The ejected connecting key 6 is stuck in the corresponding groove of the piston 9, so the sleeve 5 and the piston 9 move together in the first hydraulic chamber 4-1.

[0059] like Figure 3 As shown, the device is in working state 3. The sleeve 5 is completely separated from the piston 9, the sleeve 5 moves in the first hydraulic chamber 4-1, and the piston 9 moves in the second hydraulic chamber 4-2.

[0060] like Figure 4 As shown, the device is in operating state 4. When piston 9 enters first hydraulic chamber 4-1 and piston surface 9-B contacts sleeve surface 5-A, the "structural connection" is complete. Driven by connecting rod 8, sleeve 5 and piston 9 continue to move upward. The sensor detects this state and the control system sets the connection key to "pop-out," completing the "control connection."

[0061] The working process of the present invention is described in detail below.

[0062] The adaptive fluid inertia container for special vehicles proposed in this invention has four main working states, and its working processes are as follows:

[0063] (1) Working state 1 (see Figure 2 , the sleeve 5 and the piston 9 move together in the first hydraulic chamber 4-1, and the effective cross-sectional area of the hydraulic cylinder piston is the largest):

[0064] When a car encounters uneven road surfaces during driving, it causes the suspension to vibrate up and down. Upper lug 1 is hinged to the upper end of the vibration isolation system, while lower lug 12 is hinged to the lower end. This suspension movement causes relative compression or tension between the upper and lower lugs 1 and 12. Because upper lug 1, connecting rod 8, piston 9, and base plate 11 are integrally connected, these three components move together.

[0065] Since the bottom of the sleeve 5 is separated from the stepped portion of the hydraulic cylinder 4 at this time, the state of the connecting key is "pop-up". The pop-up connecting key 6 is stuck in the corresponding groove of the piston 9, thereby connecting the sleeve 5 and the piston 9, so that they move together in the first hydraulic chamber 4-1. This process is called "structural connection". Since the cross-sectional area of the first hydraulic chamber 4-1 is larger than the cross-sectional area of the second hydraulic chamber 4-2, the effective cross-sectional area of the hydraulic cylinder piston in this working state (this working state refers to the cross-sectional area of the first hydraulic chamber 4-1, that is, the sum of the cross-sectional areas of the sleeve 5 and the piston 9) is the largest. The volume changes of the upper and lower parts of the effective cross-sectional area of the hydraulic cylinder piston cause the fluid in the hydraulic cylinder 4 to move in the spiral pipe 15 through the upper pipe port 3-1 and the lower pipe port 3-2.

[0066] Simultaneously, the movement of base plate 11 changes the distance between the upper end of the inner wall of inertia container cylinder 16 and base plate 11, causing guide spring 13 to stretch or compress. Since spiral conduit 15 is wound around first guide spring portion 13-1 and moves with the movement of guide spring 13, the pitch and radius of spiral conduit 15 change, thereby changing the inertia coefficient of the adaptive fluid inertia container for special vehicles according to the present invention.

[0067] (2) Working state 2 (sleeve 5 and piston 9 are separated):

[0068] Sleeve 5 and piston 9 initially move downward in first hydraulic chamber 4-1. When sleeve 5 contacts the stepped portion of hydraulic cylinder barrel 4, the "control connection" state is triggered. A sensor in control box 7 detects this state and transmits a signal to the control system. The control system switches the state of connection key 6 to "retract," disengaging it from the groove in piston 9. Driven by connecting rod 8, piston 9 continues its downward movement, separating sleeve 5 from piston 9.

[0069] (3) Working state 3 (see Figure 3 , the sleeve 5 is completely separated from the piston 9, the piston 9 moves in the second hydraulic chamber 4-2, and the effective cross-sectional area of the hydraulic cylinder piston is the smallest):

[0070] The movement of the suspension causes relative compression or tension between the upper lifting eye 1 and the lower lifting eye 12. Since the upper lifting eye 1, connecting rod 8, piston 9 and bottom plate 11 are connected as a whole, the upper lifting eye 1, connecting rod 8, piston 9 and bottom plate 11 move together.

[0071] Since sleeve 5 and piston 9 are now completely separated, piston 9, driven by connecting rod 8, moves within second hydraulic chamber 4-2. The effective cross-sectional area of the hydraulic cylinder piston (in this operating state, this refers to the cross-sectional area of second hydraulic chamber 4-2, i.e., the maximum cross-sectional area of piston 9) is minimized. The volumetric variations between the upper and lower portions of the effective cross-sectional area of the hydraulic cylinder piston cause the fluid in cylinder barrel 4 to flow through upper and lower conduit openings 3-1, 3-2 and into spiral conduit 15.

[0072] Simultaneously, the movement of base plate 11 changes the distance between the upper end of the inner wall of inertia container cylinder 16 and base plate 11, causing guide spring 13 to stretch or compress. Since spiral conduit 15 is wound around first guide spring portion 13-1 and moves with the movement of guide spring 13, the pitch and radius of spiral conduit 15 change, thereby changing the inertia coefficient of the adaptive fluid inertia container for special vehicles according to the present invention.

[0073] (4) Working state 4 (see Figure 4 , sleeve 5 and piston 9 connection process):

[0074] The piston 9 initially moves upward in the second hydraulic chamber 4-2, as shown in FIG. Figure 4 (a). When the piston 9 enters the first hydraulic chamber 4-1, the piston plane 9-B contacts the sleeve plane 5-A, completing the "structural connection". The sleeve 5 and the piston 9 continue to move upward driven by the connecting rod 8. At this time, the bottom of the sleeve 5 is separated from the stepped portion of the hydraulic cylinder 4. The sensor detects this state and transmits a signal to the control system. The control system controls the state of the connection key to "pop out". The popped-out connection key is stuck in the groove of the piston 9, thereby connecting the sleeve 5 and the piston 9, completing the "control connection", and making them move together in the first hydraulic chamber 4-1, as shown in FIG. Figure 4 (b).

[0075] By analyzing the working principle of the inertia container, a dynamic model of the inertia container can be constructed:

[0076] In order to analyze the performance of the designed inertia container, the following assumptions are made when establishing the dynamic model:

[0077] (1) There is no leakage during the flow of liquid, and the system satisfies the volume conservation law;

[0078] (2) Liquids are continuous and incompressible; the density of liquids does not change with the environment and is a constant value;

[0079] (3) The effects of potential energy, heat energy loss and temperature changes on liquid properties are not considered;

[0080] (4) The mass of the piston rod is not considered;

[0081] (5) The free length of the guide spring 13 is close to the total length of the hydraulic cylinder 4.

[0082] When establishing the dynamic model, the device diagram was simplified for ease of observation without affecting the force analysis. The adaptive fluid inertia container for a special vehicle of the present invention has two states: piston 9 and sleeve 5 connected, moving together; and piston 9 and sleeve 5 separated, with the piston moving. Since the force analysis for both states is the same, the following dynamic model uses the case where piston 9 and sleeve 5 are connected and moving together to the left in the first hydraulic chamber as an example to analyze the force on piston 9 and sleeve 5. Figure 5 As shown, the force direction is horizontally to the left as positive, and the guide spring 13 is in a stretched state.

[0083] According to Newton's second law, the following relationship can be listed:

[0084] FF k -ff ΔP =F am +F ac +F ach (1)

[0085] In formula (1), F is the axial external force on the piston 9 and the sleeve 5, and the unit is N; F k is the spring force exerted on the piston 9 and the sleeve 5 when they move, in N; f is the friction force between the piston 9, the sleeve 5 and the inner wall of the hydraulic cylinder 4, in N; f ΔP is the damping force on the liquid flow, in N; F am F is the inertial force generated by the movement of the piston 9 and the sleeve 5, the unit is N; ac F is the inertial force generated by the flow of liquid in the hydraulic cylinder 4, the unit is N; ach It is the inertial force generated by the liquid flow in the spiral pipe 15, and its unit is N.

[0086] When the hydraulic fluid flows in the hydraulic cylinder 4 and the spiral pipe 15, the damping force on the fluid flow is:

[0087] f ΔP =(P2-P1)A P (2)

[0088] In formula (2), P2 is the pressure in the hydraulic cylinder 4 on the left side of the piston 9 and the sleeve 5, and the unit is Pa; P1 is the pressure in the hydraulic cylinder 4 on the right side of the piston 9 and the sleeve 5, and the unit is Pa; A P is the actual working area of the piston 9 and the sleeve 5, which is approximately the cross-sectional area A of the hydraulic cylinder 4 c Subtract the cross-sectional area A of connecting rod 8 r , the unit of all three is m 2It should be emphasized that the hydraulic cylinder 4 is divided into a first hydraulic chamber 4-1 and a second hydraulic chamber 4-2, and the cross-sectional areas of the two chambers are different. In actual calculations, the cross-sectional area of the hydraulic cylinder 4 should be determined based on the current positions of the piston 9 and sleeve 5.

[0089] According to fluid mechanics, the pressure losses at the inlet and outlet of the spiral pipe 15 and the inner wall of the spiral pipe 15 have the following relationship:

[0090] P2-P1=ΔP i +ΔP ch +ΔP o (3)

[0091] In formula (3): ΔP i is the pressure loss at the inlet of the spiral pipe 15, in Pa; ΔP ch is the pressure loss caused by the viscosity of the liquid in the spiral pipe 15, in Pa; ΔP o is the pressure loss at the outlet of the spiral pipe 15, in Pa.

[0092] Assuming that the deformation of the guide spring 13 at the current position is Δx and the elastic coefficient of the guide spring 13 is k, the pulling force exerted by the guide spring 13 on the piston 9 and the sleeve 5 is:

[0093] Fk=k·Δx (4) Substituting equations (2), (3), and (4) into equation (1), we can obtain:

[0094] F=f+ΔP ch A P +ΔP i A P +ΔP o A P +F am +F ac +F ach (5)

[0095] In formula (5), ΔP ch A P is the damping force caused by the pressure loss along the spiral pipe 15, denoted as f ch , unit is N; ΔP i A P is the damping force caused by the pressure loss at the inlet of spiral pipe 15, denoted as f i , unit is N; ΔP o A P is the damping force caused by the pressure loss at the outlet of spiral pipe 15, denoted as f o , unit is N.

[0096] For ease of understanding, the sum of the friction force, damping force and tension given by the guide spring 13 on the piston 9 is recorded as F d , the unit is N; the sum of the inertial forces is recorded as F a , the unit is N. We can get:

[0097] F=F d +F a (6)

[0098] in:

[0099]

[0100] In a fluid inertia container, the reciprocating flow of liquid in a spirally wound spiral pipe forms a "liquid flywheel". The inertia coefficient of the fluid inertia container is shown in formula (8):

[0101]

[0102] Where m is the mass of the liquid in the spiral pipe, S1 is the effective cross-sectional area of the hydraulic cylinder piston, S2 is the cross-sectional area of the spiral pipe, h is the pitch of the slender spiral pipe, and r4 is the spiral radius of the spiral pipe.

[0103] By analyzing the inertia coefficient expression of the fluid inertia container, the inertia coefficient expression of the adaptive fluid inertia container for a special vehicle of the present invention can be derived.

[0104] The inner diameter of the first hydraulic chamber 4-1 is set to d1, and the length of the cylinder is set to l1; the inner diameter of the second hydraulic chamber 4-2 is set to d2, and the length of the cylinder is set to l2. The number of turns of the guide spring 13 is n, and the outer diameter in the natural state is d t , the length in the natural state is l t The height of the piston 9 is B. The distance between the left end of the piston 9 and the left end face of the first hydraulic chamber 4-1 is l. The diameter of the connecting rod 8 is d, and the diameter of the spiral pipe 15 is d0.

[0105] The outer diameter of the guide spring 13 changes during the movement, but the change pattern is complex. Assume that the change in the outer diameter of the guide spring 13 relative to the outer diameter in the natural state at a certain moment is Δl.

[0106] Based on the assumption that the free length of the guide spring 13 is close to the total length of the hydraulic cylinder 4, it can be seen that:

[0107] l t =l1+l2 (9)

[0108] (1) When 0≤l≤l1-B:

[0109] At this time, the piston 9 is connected to the sleeve 5 and moves together in the first hydraulic chamber 4-1. At this time, the effective cross-sectional area S1 of the hydraulic cylinder piston is the largest.

[0110] The effective cross-sectional area S1 of the hydraulic cylinder piston is:

[0111]

[0112] The pitch h of the spiral pipe 15 is:

[0113]

[0114] The spiral radius r4 of the spiral pipe 15 is:

[0115]

[0116] The expression of the inertia coefficient of the adaptive fluid inertia container for a special vehicle of the present invention is:

[0117]

[0118] (2) When l1-B≤l≤l t -B:

[0119] At this time, the piston 9 is separated from the sleeve 5, and the piston 9 moves in the second hydraulic chamber 4-2. At this time, the effective cross-sectional area S1 of the hydraulic cylinder piston is the smallest.

[0120] The effective cross-sectional area S1 of the hydraulic cylinder piston is:

[0121]

[0122] The pitch h of the spiral pipe 15 is:

[0123]

[0124] The spiral radius r4 of the spiral pipe 15 is:

[0125]

[0126] The expression of the inertia coefficient of the adaptive fluid inertia container for a special vehicle of the present invention is:

[0127]

[0128] To further explore the variation law of the inertia coefficient of the adaptive fluid inertia container for a special vehicle of the present invention, the dimensions of the inertia container were designed according to the parameters of a certain car model, and the following data were obtained:

[0129]

[0130]

[0131] For ease of calculation, assume that the change in the outer diameter of the guide spring 13 during movement relative to the spring's outer diameter in its natural state is Δl = 0. Assume that the distance between the top of the piston 9 and the upper end surface of the inner wall of the first hydraulic chamber 4-1 is l. Substituting the above data into the inertia coefficient expression for the adaptive fluid inertia container for a special vehicle according to the present invention yields:

[0132] The pitch h of the guide spring 13 is:

[0133]

[0134] (1) When 0≤l≤0.055:

[0135] The expression of the inertia coefficient of the inertia container is:

[0136]

[0137] When the effective cross-sectional area of the hydraulic cylinder piston is the largest, the inertia coefficient of the inertia container changes with the piston movement as follows: Figure 6 shown.

[0138] (2) When 0.055≤l≤0.13:

[0139] The expression of the inertia coefficient of the inertia container is:

[0140]

[0141] The inertia coefficient of the inertia container when the effective cross-sectional area of the hydraulic cylinder piston is the smallest changes with the piston movement as follows: Figure 7 shown.

[0142] By analyzing the graph of the inertia coefficient of the inertia container changing with the piston motion, the following conclusions are drawn:

[0143] (1) In the adaptive fluid inertia container for a special vehicle of the present invention, the larger the effective cross-sectional area of the hydraulic cylinder piston is, the larger the inertia coefficient of the inertia container is.

[0144] (2) In the adaptive fluid inertia container for special vehicles of the present invention, when the effective cross-sectional area of the hydraulic cylinder piston is constant, the greater the distance between the top of the piston and the upper end surface of the inner wall of the first hydraulic chamber, the smaller the inertia coefficient.

[0145] In summary, the change law of the adaptive fluid inertia container of a special vehicle according to the present invention as the suspension moves is as follows:

[0146] When suspension movement causes relative compression between the upper and lower lifting lugs, the connecting rod 8 of the adaptive fluid inertia container for a special vehicle of the present invention moves downward. As the distance between the top end of the piston 9 and the upper end surface of the inner wall of the first hydraulic chamber 4-1 increases, the inertia coefficient gradually decreases. When suspension movement causes relative tension between the upper and lower lifting lugs, the connecting rod 8 of the adaptive fluid inertia container for a special vehicle of the present invention moves upward. As the distance between the top end of the piston 9 and the upper end surface of the inner wall of the first hydraulic chamber decreases, the inertia coefficient gradually increases.

[0147] The embodiments described are preferred implementations of the present invention, but the present invention is not limited to the above implementations. Any obvious improvements, substitutions or modifications that can be made by those skilled in the art without departing from the essence of the present invention are within the scope of protection of the present invention.

Claims

1. A special vehicle adaptive fluid inertia container, characterized in that: It includes a pipe port (3), a hydraulic cylinder (4), a connecting rod (8), a piston (9), a base plate (11), a guide spring (13), a spiral pipe (15), and an inertia cylinder (16); The upper end of the inertial cylinder (16) is provided with a through hole, in which a connecting rod (8) is accommodated, a piston (9) is fixed on the connecting rod (8), and the connecting rod (8) extends upward from the through hole. The hydraulic cylinder (4) is fixedly connected to the upper part of the inertial cylinder (16), and the upper end of the hydraulic cylinder (4) is also provided with a through hole, in which a connecting rod (8) is accommodated, and the connecting rod (8) extends upward from the through hole. The lower end of the hydraulic cylinder (4) is also provided with a through hole, in which a connecting rod (8) is accommodated, and the connecting rod (8) extends downward from the through hole. The lower end of the connecting rod (8) is fixedly connected to the bottom plate (11). The hydraulic cylinder (4) is designed in a stepped manner and is divided into a first hydraulic chamber (4-1) and a second hydraulic chamber (4-2). An upper pipe opening (3-1) is provided at the upper end of the first hydraulic chamber (4-1), and a lower pipe opening (3-2) is provided at the lower end of the second hydraulic chamber (4-2). The upper pipe opening (3-1) and the lower pipe opening (3-2) are connected via a spiral pipe (15). The guide spring (13) is arranged along the outer periphery of the hydraulic cylinder (4) and is divided into a first guide spring portion (13-1) and a second guide spring portion (13-2). The upper end of the guide spring (13) is fixed to the lower end inside the inertia cylinder (16), and the lower end is fixed to the bottom plate (11); wherein, a spiral pipe (15) is wound around the outer end of the first guide spring portion (13-1).

2. The adaptive fluid inertia container for special vehicles according to claim 1, characterized in that: in, The sleeve (5) is slidably mounted on the inner wall of the first hydraulic chamber (4-1), and a connecting key (6) and a control box (7) are fixedly mounted in the sleeve (5); The control box (7) is equipped with a control system and a sensor. The control system controls the state of the connection key (6) according to the signal collected by the sensor: "pop-up" and "retract". The sensor is installed at the bottom of the sleeve (5) and mainly monitors whether the bottom of the sleeve (5) contacts the stepped portion of the hydraulic cylinder (4); if the bottom of the sleeve (5) contacts the stepped portion of the hydraulic cylinder (4), the control system controls the state of the connection key to be "retracted"; if the bottom of the sleeve (5) is separated from the stepped portion of the hydraulic cylinder (4), the control system controls the state of the connection key to be "ejected".

3. The adaptive fluid inertia container for special vehicles according to claim 2, characterized in that: in, The first hydraulic chamber (4-1) is located above the second hydraulic chamber (4-2), and the volume of the first hydraulic chamber (4-1) is larger than that of the second hydraulic chamber (4-2).

4. The adaptive fluid inertia container for special vehicles according to claim 3, characterized in that: in, The piston (9) has an I-shaped cross section and includes a small diameter portion (9-1) and a large diameter portion (9-2); the outer diameter of the large diameter portion (9-2) is the same as the inner diameter of the second hydraulic chamber (4-2), and the outer diameter of the large diameter portion (9-2) is larger than the minimum inner diameter of the sleeve (5); the outer diameter of the small diameter portion (9-1) is smaller than the inner diameter of the second hydraulic chamber (4-2), and the small diameter portion (9-1) and the large diameter portion (9-2) are formed with grooves.

5. The adaptive fluid inertia container for special vehicles according to any one of claims 1 to 4, characterized in that: The lower end of the inertia container cylinder (16) is fixedly connected to a lower lifting lug (12), which is fixedly connected to the lower end point of the vibration isolation system; the upper end of the connecting rod (8) is fixedly connected to an upper lifting lug (1), which is fixedly connected to the upper end point of the vibration isolation system.

6. The adaptive fluid inertia container for a special vehicle according to any one of claims 2 to 4, characterized in that: An upper buffer spring (2) is also provided inside the hydraulic cylinder (4) to relieve the impact of the sleeve (5) and the piston (9) on the hydraulic cylinder (4) when the sleeve (5) and the piston (9) move upward; a lower buffer spring (10) is also provided inside the lower part of the hydraulic cylinder (4) to relieve the impact of the piston (9) on the hydraulic cylinder (4) when the piston (9) moves downward.

7. The adaptive fluid inertia container for special vehicles according to any one of claims 2 to 4, characterized in that: When the inertia container is working, a sealing ring I (14) is installed on the outer end of the sleeve (5).

8. The adaptive fluid inertia container for special vehicles according to any one of claims 1 to 4, characterized in that: A sealing ring II (17) is installed at the connection between the inertia container barrel (16), the hydraulic cylinder barrel (4) and the connecting rod (8).

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