Configuration-variable suspension

Abstract

The utility model relates to a variable-configuration suspension, which comprises one or more double-axle modules comprising two axles and / or one or more single-axle modules comprising one axle, and the double-axle modules and the single-axle modules comprise a plurality of hydraulic cylinders provided with rodless cavities and rod cavities, connection or disconnection is established between rodless cavities and rod cavities of different hydraulic cylinders through a connecting loop composed of oil pipes. The connecting loop comprises a plurality of servo valves, a plurality of hydraulic cylinders and a plurality of hydraulic cylinders, one or more reversing valves; the first hydraulic branch pipe and the second hydraulic branch pipe are connected to a rodless cavity and a rod cavity of the first hydraulic cylinder respectively, the fifth hydraulic branch pipe and the sixth hydraulic branch pipe are connected to a rodless cavity and a rod cavity of the third hydraulic cylinder respectively, the first reversing valve is arranged at the joint of the four hydraulic branch pipes, and the second reversing valve is arranged at the joint of the four hydraulic branch pipes. The hydraulic branch pipes are connected to the first hydraulic cylinder to switch the communication state between the first hydraulic cylinder and the third hydraulic cylinder, and the hydraulic main pipes connected with the hydraulic branch pipes can be connected to the corresponding servo valves.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicle suspensions, and particularly relates to a variable configuration suspension. Background Art

[0002] An automotive suspension is a key component in a vehicle chassis. Its main functions are to support the vehicle body, mitigate shocks and vibrations caused by uneven road surfaces, and ensure good contact between the wheels and the road surface.

[0003] CN206812740U discloses an anti-roll suspension system, which includes a suspension cross arm, a first elastic member and a second elastic member respectively arranged at the lower end of the vehicle body. It also includes an ECU, a mode switching valve and an accumulator switching valve electrically connected to the ECU. The first elastic member includes a first hydraulic cylinder and a first accumulator. The upper chamber of the first hydraulic cylinder and the first accumulator are respectively connected to both ends of a first hydraulic oil circuit. The second elastic member includes a second hydraulic cylinder and a second accumulator. The second accumulator is connected to one end of a third hydraulic oil circuit and a fourth hydraulic oil circuit through the accumulator switching valve. The other ends of the third hydraulic oil circuit and the fourth hydraulic oil circuit are respectively connected to the upper chamber and the lower chamber of the second hydraulic cylinder. The mode switching valve is connected to the first hydraulic oil circuit, the third hydraulic oil circuit, the fourth hydraulic oil circuit, and the lower chamber of the first hydraulic cylinder. The ECU is used to control the mode switching valve and the accumulator switching valve to switch the suspension system among three states of being disconnected from each other, cross-connected, and parallel-connected.

[0004] Most of the existing technologies have problems such as a single working mode or an unchangeable configuration of the suspension system between vehicle axles. Even though the suspension system disclosed in the above-mentioned existing technology can be switched among three states of being disconnected from each other, cross-connected, and parallel-connected, its configuration changes less and it is difficult to cope with complex road conditions. In addition, most of the existing suspension systems are customized designs, which are difficult to achieve efficient modular assembly and cannot meet various different forms of requirements, especially for multi-axle road vehicles.

[0005] In addition, on the one hand, there are differences in the understanding of those skilled in the art; on the other hand, although the applicant has studied a large number of documents and patents when making the present utility model, all details and contents are not listed in detail due to space limitations. However, this does not mean that the present utility model does not have the features of these existing technologies. On the contrary, the present utility model already has all the features of the existing technologies, and the applicant reserves the right to add relevant existing technologies in the background art. Summary of the Utility Model

[0006] Aiming at the deficiencies of the existing technology, the present utility model provides a variable configuration suspension to solve at least some of the above technical problems.

[0007] The utility model discloses a variable configuration suspension, which comprises: one or more double-axle modules each containing two axles and / or one or more single-axle modules each containing one axle. The double-axle modules and the single-axle modules comprise: a plurality of hydraulic cylinders configured with rodless cavities and rod cavities, and connection or disconnection between the rodless cavities and the rod cavities of different hydraulic cylinders is established through a connection loop composed of oil pipes. The connection loop comprises: a plurality of servo valves; one or more reversing valves; a plurality of hydraulic branch pipes and a hydraulic main pipe. Preferably, a first hydraulic branch pipe and a second hydraulic branch pipe are respectively connected to the rodless cavity and the rod cavity of a first hydraulic cylinder, a fifth hydraulic branch pipe and a sixth hydraulic branch pipe are respectively connected to the rodless cavity and the rod cavity of a third hydraulic cylinder, and a first reversing valve is arranged at the connection of the first hydraulic branch pipe, the second hydraulic branch pipe, the fifth hydraulic branch pipe and the sixth hydraulic branch pipe to switch the communication state between the first hydraulic cylinder and the third hydraulic cylinder located on the same axle. A first hydraulic main pipe and a second hydraulic main pipe respectively connected to the first hydraulic branch pipe and the second hydraulic branch pipe are both connected to a first servo valve, and a fifth hydraulic main pipe and a sixth hydraulic main pipe respectively connected to the fifth hydraulic branch pipe and the sixth hydraulic branch pipe are connected to a third servo valve.

[0008] The suspension of the utility model is particularly applicable to multi-axle road vehicles. When the suspension is configured on a multi-axle road vehicle, the combination form of the suspension can be determined based on the number of axles of the multi-axle road vehicle, wherein the suspension can comprise double-axle modules and / or single-axle modules. For the suspension of a multi-axle road vehicle, its multi-axle structure can be composed of combined double-axle modules or combined single-axle modules or a hybrid combination of double-axle modules and single-axle modules, making the configuration more flexible and allowing modular assembly according to actual needs. Further, each servo valve of the variable configuration suspension can work in multiple orientations, and each reversing valve can work in multiple orientations, so that the communication relationship between the rodless cavities and the rod cavities of each hydraulic cylinder is adjusted based on the combination of different working orientations of the servo valves and the reversing valves. The utility model adjusts the communication relationship between the rodless cavities and the rod cavities of each hydraulic cylinder by adjusting the working orientations of the servo valves and the reversing valves, thereby realizing a rapid and smooth switch between multiple configurations of the suspension and making up for the deficiencies of the traditional interconnected suspension system and non-interconnected suspension system in terms of single vehicle motion control mode and configuration.

[0009] According to a preferred embodiment, the servo valves and the reversing valves comprise three working orientations, and by switching the working orientations, the four oil circuits connected to the servo valves and the reversing valves are switched between the states of parallel interconnection, cross interconnection, and mutual disconnection.

[0010] According to a preferred embodiment, for a biaxial module, the reversing valve includes a third reversing valve for switching the communication state between the second hydraulic cylinder and the fourth hydraulic cylinder on the same axle. Among them, the third hydraulic branch pipe and the fourth hydraulic branch pipe are respectively connected to the rodless cavity and the rod chamber of the second hydraulic cylinder, the seventh hydraulic branch pipe and the eighth hydraulic branch pipe are respectively connected to the rodless cavity and the rod chamber of the fourth hydraulic cylinder, and the third reversing valve is arranged at the connection of the third hydraulic branch pipe, the fourth hydraulic branch pipe, the seventh hydraulic branch pipe and the eighth hydraulic branch pipe.

[0011] According to a preferred embodiment, for a biaxial module, the servo valve includes a second servo valve and a fourth servo valve. Among them, the third hydraulic main pipe and the fourth hydraulic main pipe respectively connected to the third hydraulic branch pipe and the fourth hydraulic branch pipe are both connected to the second servo valve, and the seventh hydraulic main pipe and the eighth hydraulic main pipe respectively connected to the seventh hydraulic branch pipe and the eighth hydraulic branch pipe are connected to the fourth servo valve.

[0012] According to a preferred embodiment, for a biaxial module, the reversing valve includes a second reversing valve, and the second reversing valve is respectively connected to the first hydraulic main pipe, the second hydraulic main pipe, the third hydraulic main pipe, and the fourth hydraulic main pipe through the first hydraulic bypass pipe, the second hydraulic bypass pipe, the third hydraulic bypass pipe, and the fourth hydraulic bypass pipe.

[0013] According to a preferred embodiment, for a biaxial module, the servo valve includes a first servo valve, a second servo valve, a third servo valve, and a fourth servo valve, and the reversing valve includes a first reversing valve, a second reversing valve, and a third reversing valve. Among them, based on the driving state of the biaxial module, by adjusting the working positions of each servo valve and / or each reversing valve, the biaxial module is switched between a parallel interconnection configuration, a cross interconnection configuration, a pitch interconnection configuration, and / or an independent disconnection configuration.

[0014] The parallel interconnection configuration can achieve the control of the vertical movement of the vehicle by the biaxial module; the cross interconnection configuration can achieve the control of the roll movement of the vehicle by the biaxial module; the pitch interconnection configuration can achieve the control of the vertical movement and the pitch movement of the vehicle by the biaxial module; the independent disconnection configuration can achieve the independent control of each hydraulic cylinder by the biaxial module.

[0015] According to a preferred embodiment, for the biaxial module in the first driving state, each servo valve is adjusted to work in the left position or the right position, and the reversing valve is adjusted to work in the lower position or the middle position, so that the biaxial module is switched to the parallel interconnection configuration in the first driving state; each servo valve is adjusted to work in the left position or the right position, and the reversing valve is adjusted to work in the upper position or the middle position, so that the biaxial module is switched to the cross interconnection configuration in the first driving state; each servo valve is adjusted to work in the left position or the right position, and the reversing valve is adjusted to work in the lower position or the middle position, so that the biaxial module is switched to the pitch interconnection configuration in the first driving state; each servo valve is adjusted to work in the left position or the right position, and the reversing valve is adjusted to work in the middle position, so that the biaxial module is switched to the independent disconnection configuration in the first driving state. Further, in the parallel interconnection configuration and the independent disconnection configuration, each servo valve is in the same working orientation; in the cross interconnection configuration, the first servo valve and the second servo valve are in the same working orientation and opposite to the working orientations of the third servo valve and the fourth servo valve; in the pitch interconnection configuration, the first servo valve and the third servo valve are in the same working orientation and opposite to the working orientations of the second servo valve and the fourth servo valve.

[0016] According to a preferred embodiment, for the biaxial module in the second driving state, each servo valve is adjusted to work in the middle position, and the reversing valve is adjusted to work in the lower position or the right position, so that the biaxial module is switched to the parallel interconnection configuration in the second driving state; each servo valve is adjusted to work in the middle position, and the reversing valve is adjusted to work in the upper position or the right position, so that the biaxial module is switched to the cross interconnection configuration in the second driving state; each servo valve is adjusted to work in the middle position, and the reversing valve is adjusted to work in the lower position or the left position, so that the biaxial module is switched to the pitch interconnection configuration in the second driving state.

[0017] According to a preferred embodiment, for the uniaxial module, the servo valve includes a first servo valve and a third servo valve, and the reversing valve includes a first reversing valve. Among them, based on the driving state of the uniaxial module, the working orientation of each servo valve and / or each reversing valve is adjusted to enable the uniaxial module to switch between the parallel interconnection configuration, the cross interconnection configuration, and / or the independent disconnection configuration.

[0018] The parallel interconnection configuration can achieve the control of the vertical movement of the vehicle by the uniaxial module; the cross interconnection configuration can achieve the control of the roll movement of the vehicle by the uniaxial module; the independent disconnection configuration can achieve the independent control of each hydraulic cylinder by the uniaxial module.

[0019] According to a preferred embodiment, for a single-axis module in the first driving state, each servo valve is adjusted to work in the left or right position, and the first reversing valve is adjusted to work in the lower position, so that the single-axis module is switched to the parallel interconnection configuration in the first driving state; each servo valve is adjusted to work in the left or right position, and the first reversing valve is adjusted to work in the upper position, so that the single-axis module is switched to the cross interconnection configuration in the first driving state; each servo valve is adjusted to work in the left or right position, and the reversing valve is adjusted to work in the middle position, so that the single-axis module is switched to the independent disconnection configuration in the first driving state. Further, in the parallel interconnection configuration and the independent disconnection configuration, each servo valve is in the same working orientation; in the cross interconnection configuration, the working orientations of the first servo valve and the third servo valve are opposite.

[0020] According to a preferred embodiment, for a single-axis module in the second driving state, each servo valve is adjusted to work in the middle position, and the first reversing valve is adjusted to work in the lower position, so that the single-axis module is switched to the parallel interconnection configuration in the second driving state; each servo valve is adjusted to work in the middle position, and the first reversing valve is adjusted to work in the upper position, so that the single-axis module is switched to the cross interconnection configuration in the second driving state.

[0021] According to a preferred embodiment, the servo valve is connected to the opposite end of the corresponding hydraulic branch pipe through a hydraulic main pipe and is connected to a power source through an oil pipe. The power source includes an oil tank, a filter, a hydraulic pump and a motor. The motor can drive the hydraulic pump to operate to drive the oil in the oil tank to enter the first oil pipe equipped with a first check valve through the filter, and the returned oil enters the oil tank through the second oil pipe equipped with a second check valve. Both ends of the pressure limiting valve are respectively connected to the first oil pipe and the second oil pipe.

[0022] The power source can provide power for the oil flow in the suspension, so that the oil can flow in the oil pipes of the connection circuit. When the power source is started, the suspension is in the second driving state; when the power source is turned off, the suspension is in the first driving state. The suspension in different driving states can be based on the combination of different working orientations of the servo valve and the reversing valve, so that the vehicle can be controlled when the vehicle undergoes vertical movement, roll movement, pitch movement and / or vehicle body warping movement or the wheel grounding performance deteriorates significantly.

[0023] The pressure limiting valve can be configured as a pressure reducing valve to limit the maximum system pressure, so as to avoid phenomena such as oil pipe rupture caused by excessive system oil pressure when the system is in a fault state. The check valve can prevent the oil from flowing back.

[0024] The connection circuit includes a damping valve provided on the oil pipe. The rodless chambers and rod chambers of each hydraulic cylinder can be respectively communicated with hydraulic branch pipes provided with corresponding damping valves, and each hydraulic branch pipe can be connected to a corresponding hydraulic main pipe, so as to change the connection relationship between each hydraulic main pipe and / or hydraulic branch pipe by adjusting the working positions of each servo valve and / or each reversing valve. Description of the Drawings

[0025] Figure 1 Schematic diagram of the biaxial module structure of the variable configuration suspension;

[0026] Figure 2 Schematic diagram of the uniaxial module structure of the variable configuration suspension;

[0027] Figure 3 Schematic diagram of the multi-axis structure after combining the variable configuration suspension with biaxial modules;

[0028] Figure 4 Schematic diagram of the multi-axis structure after combining the variable configuration suspension with uniaxial modules;

[0029] Figure 5 Schematic diagram of the multi-axis structure after combining the variable configuration suspension with a mixture of uniaxial and biaxial modules;

[0030] Figure 6 Schematic diagram of the corner module structure of the variable configuration suspension.

[0031] List of Reference Numerals

[0032] 1: Motor; 2: Hydraulic pump; 3: Filter; 4: Oil tank; 5: Pressure limiting valve; 6: Controller; 11: First hydraulic cylinder; 12: Second hydraulic cylinder; 13: Third hydraulic cylinder; 14: Fourth hydraulic cylinder; 21: First damping valve; 22: Second damping valve; 23: Third damping valve; 24: Fourth damping valve; 25: Fifth damping valve; 26: Sixth damping valve; 27: Seventh damping valve; 28: Eighth damping valve; 29-a: First check valve; 29-b: Second check valve; 31: First accumulator; 32: Second accumulator; 33: Third accumulator; 34: Fourth accumulator; 35: Fifth accumulator; 36: Sixth accumulator; 37: Seventh accumulator; 38: Eighth accumulator; 39-a: Ninth accumulator; 39-b: Tenth accumulator; 41: First reversing valve; 42: Second reversing valve; 43: Third reversing valve; 51: First servo valve; 52: Second servo valve; 53: Third servo valve; 54: Fourth servo valve. Detailed Description of the Preferred Embodiments

[0033] The following is a detailed description with reference to the accompanying drawings.

[0034] As Figures 1 to 5As shown, the present utility model discloses a variable configuration suspension, which may include one or more double-axis modules and / or one or more single-axis modules, and is particularly applicable to multi-axis road vehicles. Preferably, for multi-axis road vehicles with an even number of axles, the suspension may adopt a multi-axis structure formed by combining multiple double-axis modules; for multi-axis road vehicles with an odd number of axles, the suspension may adopt a multi-axis structure formed by a hybrid combination of single-axis modules and double-axis modules. Preferably, a suspension adopting a multi-axis structure formed by combining multiple single-axis modules can be used for both multi-axis road vehicles with an even number of axles and those with an odd number of axles.

[0035] Preferably, as Figure 1 and Figure 2 shown, both the double-axis module and the single-axis module may include hydraulic cylinders arranged on one side of the wheels mounted on each axle. The hydraulic cylinders are arranged between the vehicle body and the wheels, and each hydraulic cylinder can be combined and connected in various configurations through a connection circuit composed of oil pipes. Further, the connection circuit may include: a damping valve, an accumulator, a reversing valve, a servo valve, a controller 6, a pressure limiting valve 5, and a power source.

[0036] Preferably, as Figure 1 and Figure 2 shown, the power source includes an oil tank 4, a filter 3, a hydraulic pump 2, and a motor 1. Further, the hydraulic pump 2 can be a unidirectional or bidirectional pump, and the motor 1 can be driven forward or generate electricity in reverse.

[0037] Preferably, as Figure 1 and Figure 2 shown, the pressure limiting valve 5 can be configured as a pressure reducing valve to limit the maximum system pressure, thereby avoiding phenomena such as oil pipe rupture caused by excessive system oil pressure when the system is in a fault state. Further, the connection circuit may also include a first check valve 29-a and a second check valve 29-b. Among them, the first check valve 29-a and the second check valve 29-b are respectively arranged on the oil pipes connected to both ends of the pressure limiting valve 5. Further, the first check valve 29-a can be arranged on the first oil pipe, and the second check valve 29-b can be arranged on the second oil pipe. Among them, the first oil pipe can be connected to the hydraulic pump 2, and the first oil pipe can be configured as a high-pressure oil pipe, and the second oil pipe can be configured as a low-pressure oil pipe.

[0038] Preferably, as Figure 1 shown, for the double-axis module, the hydraulic cylinders may include a first hydraulic cylinder 11, a second hydraulic cylinder 12, a third hydraulic cylinder 13, and a fourth hydraulic cylinder 14.

[0039] Preferably, as Figure 1As shown, for the biaxial module, the damping valve may include a first damping valve 21, a second damping valve 22, a third damping valve 23, a fourth damping valve 24, a fifth damping valve 25, a sixth damping valve 26, a seventh damping valve 27, and an eighth damping valve 28. Among them, the first damping valve 21 and the second damping valve 22 communicate with the first hydraulic cylinder 11; the third damping valve 23 and the fourth damping valve 24 communicate with the second hydraulic cylinder 12; the fifth damping valve 25 and the sixth damping valve 26 communicate with the third hydraulic cylinder 13; the seventh damping valve 27 and the eighth damping valve 28 communicate with the fourth hydraulic cylinder 14.

[0040] Preferably, as Figure 1 shown, for the biaxial module, the accumulator may include a first accumulator 31, a second accumulator 32, a third accumulator 33, a fourth accumulator 34, a fifth accumulator 35, a sixth accumulator 36, a seventh accumulator 37, and an eighth accumulator 38. Among them, the first accumulator 31 is connected to the oil pipe provided with the first damping valve 21; the second accumulator 32 is connected to the oil pipe provided with the second damping valve 22; the third accumulator 33 is connected to the oil pipe provided with the third damping valve 23; the fourth accumulator 34 is connected to the oil pipe provided with the fourth damping valve 24; the fifth accumulator 35 is connected to the oil pipe provided with the fifth damping valve 25; the sixth accumulator 36 is connected to the oil pipe provided with the sixth damping valve 26; the seventh accumulator 37 is connected to the oil pipe provided with the seventh damping valve 27; the eighth accumulator 38 is connected to the oil pipe provided with the eighth damping valve 28. Preferably, the accumulator may further include a ninth accumulator 39-a and a tenth accumulator 39-b. Among them, the ninth accumulator 39-a may be connected to the first oil pipe, and the tenth accumulator 39-b may be connected to the second oil pipe.

[0041] Preferably, as Figure 1 shown, for the biaxial module, the servo valve may include a first servo valve 51, a second servo valve 52, a third servo valve 53, and a fourth servo valve 54, and the reversing valve may include a first reversing valve 41, a second reversing valve 42, and a third reversing valve 43.

[0042] Preferably, the servo valve may have three working positions, including a first working position for cross-connecting the oil circuits connected to both ends of the servo valve, a second working position for disconnecting the oil circuits connected to both ends of the servo valve, and a third working position for parallel-connecting the oil circuits connected to both ends of the servo valve. Further, based on the arrangement of the servo valve, the above three working positions can be represented by a relative position relationship. Among them, when the servo valve is arranged horizontally, the first working position is the left position, the second working position is the middle position, and the third working position is the right position.

[0043] Preferably, the reversing valve may have three working positions, including a fourth working position for cross-connecting the oil circuits connected to both ends of the reversing valve, a fifth working position for disconnecting the oil circuits connected to both ends of the reversing valve, and a sixth working position for parallel-connecting the oil circuits connected to both ends of the reversing valve. Further, based on the arrangement of the reversing valve, the above three working positions can be represented by a relative position relationship. Among them, when the reversing valve is arranged horizontally, the fourth working position is the left position, the fifth working position is the middle position, and the sixth working position is the right position; when the reversing valve is arranged vertically, the fourth working position is the upper position, the fifth working position is the middle position, and the sixth working position is the lower position.

[0044] Preferably, as Figure 1 shown, for the dual-axis module, various configuration switches can be achieved by adjusting the working positions of the reversing valve and the servo valve. Among them, the specific switching strategy can be shown in Table 1.

[0045] Table 1 Configuration Switching Comparison Table of Dual-Axis Module

[0046]

[0047] Preferably, as Figure 1 shown, for the dual-axis module, all servo valves are in the middle working position, and the reversing valve works in the lower or right position, so that the dual-axis module can form a parallel interconnection configuration in the second driving state. Preferably, when the dual-axis module is in the parallel interconnection configuration in the second driving state, the motor 1 and the hydraulic pump 2 do not work. At this time, the rodless cavities of the first hydraulic cylinder 11, the second hydraulic cylinder 12, the third hydraulic cylinder 13, and the fourth hydraulic cylinder 14 are interconnected through oil pipes, and the rod cavities are interconnected through oil pipes. Preferably, incompressible hydraulic oil is used as the force transmission medium, and when the vehicle body and the wheels move relatively vertically, it flows through the damping valve and the accumulator in the suspension system.

[0048] Preferably, as Figure 1 shown, for the dual-axis module, all servo valves are in the middle working position, and the reversing valve works in the upper or right position, so that the dual-axis module can form a cross-interconnection configuration in the first driving state. Preferably, when the dual-axis module is in the cross-interconnection configuration in the second driving state, the motor 1 and the hydraulic pump 2 do not work. At this time, the rodless cavities of the left first hydraulic cylinder 11 and the second hydraulic cylinder 12 are interconnected with the rod cavities of the right third hydraulic cylinder 13 and the fourth hydraulic cylinder 14 through oil pipes; or the rod cavities of the left first hydraulic cylinder 11 and the second hydraulic cylinder 12 are interconnected with the rodless cavities of the right third hydraulic cylinder 13 and the fourth hydraulic cylinder 14 through oil pipes. Preferably, incompressible hydraulic oil is used as the force transmission medium, and when the vehicle body and the wheels move relatively laterally, it flows through the damping valve and the accumulator in the suspension system.

[0049] Preferably, asFigure 1 As shown, for the dual-axis module, all servo valves are in the neutral position, and the reversing valve is in the lower position or the left position, so that the dual-axis module can form a pitch interconnection configuration in the first driving state. Preferably, when the dual-axis module is in the pitch interconnection configuration in the second driving state, the motor 1 and the hydraulic pump 2 do not work. At this time, the rodless chambers of the upper first hydraulic cylinder 11 and the third hydraulic cylinder 13 are interconnected with the rod chambers of the lower second hydraulic cylinder 12 and the fourth hydraulic cylinder 14 through oil pipes; or the rod chambers of the upper first hydraulic cylinder 11 and the third hydraulic cylinder 13 are interconnected with the rodless chambers of the lower second hydraulic cylinder 12 and the fourth hydraulic cylinder 14 through oil pipes. Preferably, incompressible hydraulic oil is used as the force transmission medium, and when the vehicle body and the wheels undergo relative pitch motion, it flows through the damping valve and the accumulator in the suspension system.

[0050] Preferably, as Figure 1 As shown, for the dual-axis module, all servo valves are in the left position or the right position, and the reversing valve is in the lower position or the neutral position, so that the dual-axis module can form a parallel interconnection configuration in the second driving state. Preferably, when the dual-axis module is in the parallel interconnection configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipes. Specifically, if the vehicle body is to be lifted, all servo valves are in the left position; conversely, if the vehicle body is to be lowered, all servo valves are in the right position. At this time, the rodless chambers of the four hydraulic cylinders are interconnected through oil pipes, and the rod chambers are interconnected through oil pipes. Further, when the vehicle body is lifted, the motor 1 drives the hydraulic pump 2 to pump the hydraulic oil in the fuel tank 4 into the rodless chambers of all hydraulic cylinders. Further, the working volume in the rod chambers of all hydraulic cylinders decreases, causing some hydraulic oil to be squeezed out, and after flowing through the damping valve and the servo valve, it returns to the inside of the fuel tank 4 through the second oil pipe. Preferably, when the vehicle body is lowered, the motor 1 drives the hydraulic pump 2 to pump the hydraulic oil in the fuel tank 4 into the rod chambers of all hydraulic cylinders. Further, the working volume in the rodless chambers of all hydraulic cylinders decreases, causing some hydraulic oil to be squeezed out, and after flowing through the damping valve and the servo valve, it returns to the inside of the fuel tank 4 through the second oil pipe.

[0051] Preferably, as Figure 1As shown in the figure, for the dual-axis module, all servo valves are operated in the left or right position, and the reversing valve is operated in the upper or middle position, so that the dual-axis module can form a cross-interconnection configuration in the second driving state. Preferably, when the dual-axis module is in the cross-interconnection configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if the vehicle body is to be controlled for forward roll, the two servo valves on the left side are both operated in the left position, and the two servo valves on the right side are both operated in the right position; conversely, if the vehicle body is to be controlled for reverse roll, the two servo valves on the left side are both operated in the right position, and the two servo valves on the right side are both operated in the left position. At this time, the rodless chambers of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 on the left side are interconnected with the rod chambers of the third hydraulic cylinder 13 and the fourth hydraulic cylinder 14 on the right side through the oil pipe, and the rod chambers of the first hydraulic cylinder 11 and the second hydraulic cylinder 12 on the left side are interconnected with the rodless chambers of the third hydraulic cylinder 13 and the fourth hydraulic cylinder 14 on the right side through the oil pipe.

[0052] Preferably, as Figure 1 shown in the figure, for the dual-axis module, all servo valves are operated in the left or right position, and the reversing valve is operated in the lower or middle position, so that the dual-axis module can form a pitch-interconnection configuration in the second driving state. Preferably, when the dual-axis module is in the pitch-interconnection configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if the vehicle body is to be controlled for raising the head, the two servo valves on the upper side are both operated in the left position, and the two servo valves on the lower side are both operated in the right position; conversely, if the vehicle body is to be controlled for nodding, the two servo valves on the upper side are both operated in the right position, and the two servo valves on the lower side are both operated in the left position. At this time, the rodless chambers of the first hydraulic cylinder 11 and the third hydraulic cylinder 13 on the upper side are interconnected with the rod chambers of the second hydraulic cylinder 12 and the fourth hydraulic cylinder 14 on the lower side through the oil pipe, and the rod chambers of the first hydraulic cylinder 11 and the third hydraulic cylinder 13 on the upper side are interconnected with the rodless chambers of the second hydraulic cylinder 12 and the fourth hydraulic cylinder 14 on the lower side through the oil pipe.

[0053] Preferably, as Figure 1 shown in the figure, for the dual-axis module, all reversing valves are operated in the middle position, and the servo valves are operated in the left or right position, so that the dual-axis module can form an independent disconnection configuration in the second driving state. At this time, the dual-axis module can be regarded as a combination of angular modules as Figure 6 shown in the figure. Preferably, when the dual-axis module is in the independent disconnection configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if the vehicle body on the left front side (left rear side, right front side, right rear side) is to be raised, the servo valve on the left front side (left rear side, right front side, right rear side) is operated in the left position; conversely, if the vehicle body on the left front side (left rear side, right front side, right rear side) is to be lowered, the servo valve on the left front side (left rear side, right front side, right rear side) is operated in the right position. At this time, the rodless chamber and the rod chamber of a single hydraulic cylinder are independent of each other.

[0054] Preferably, as Figure 2 shown, for a single-axis module, the hydraulic cylinder may include a first hydraulic cylinder 11 and a third hydraulic cylinder 13.

[0055] Preferably, as Figure 2 shown, for a single-axis module, the damping valve may include a first damping valve 21, a second damping valve 22, a fifth damping valve 25, and a sixth damping valve 26.

[0056] Preferably, as Figure 2 shown, for a single-axis module, the accumulator may include a first accumulator 31, a second accumulator 32, a fifth accumulator 35, and a sixth accumulator 36. Preferably, the accumulator may further include a ninth accumulator 39-a and a tenth accumulator 39-b, wherein the ninth accumulator 39-a may be connected to the first oil pipe, and the tenth accumulator 39-b may be connected to the second oil pipe.

[0057] Preferably, as Figure 2 shown, for a single-axis module, the servo valve may include a first servo valve 51 and a third servo valve 53, and the reversing valve may include a first reversing valve 41. Preferably, the working positions of the servo valve and the reversing valve of the single-axis module are the same as those of the double-axis module.

[0058] Preferably, as Figure 2 shown, for a single-axis module, the switching between multiple configurations can be achieved by adjusting the working positions of the reversing valve and the servo valve, and the specific switching strategy is shown in Table 2.

[0059] Table 2 Configuration Switching Comparison Table of Single-Axis Module

[0060]

[0061] Preferably, as Figure 2 shown, for a single-axis module, all servo valves are in the neutral working position, and the reversing valve works in the lower position, so that the single-axis module can form a parallel interconnection configuration in the second driving state. At this time, the rodless chambers of the left and right hydraulic cylinders are interconnected through oil pipes, and the rod chambers are interconnected through oil pipes. Preferably, incompressible hydraulic oil is used as the force transmission medium, and when the vehicle body and the wheels move relatively vertically, it flows through the damping valve and the accumulator in the single-axis module structure of the suspension system.

[0062] Preferably, as Figure 2As shown, for the single-axis module, all servo valves are in the neutral position, and the reversing valve is in the upper position, so that the single-axis module can form a cross-interconnected configuration in the second driving state. At this time, the rodless cavity of the left hydraulic cylinder (i.e., the first hydraulic cylinder 11) is interconnected with the rod cavity of the right hydraulic cylinder (i.e., the third hydraulic cylinder 13) through a oil pipe; the rod cavity of the left hydraulic cylinder (i.e., the first hydraulic cylinder 11) is interconnected with the rodless cavity of the right hydraulic cylinder (i.e., the third hydraulic cylinder 13) through a oil pipe. Preferably, incompressible hydraulic oil is used as the force transmission medium, which flows through the damping valve and accumulator in the structure of the single-axis module of the suspension system when the vehicle body and wheels undergo relative roll motion.

[0063] Preferably, as Figure 2 shown, for the single-axis module, all servo valves are in the left or right position, and the reversing valve is in the lower position, so that the single-axis module can form a parallel-interconnected configuration in the first driving state. Preferably, when the single-axis module is in the parallel-interconnected configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if it is desired to raise the hydraulic cylinders on both sides, all servo valves are in the left position; conversely, if it is desired to lower the hydraulic cylinders on both sides, all servo valves are in the right position. At this time, the rodless cavities of the hydraulic cylinders on both sides are interconnected through a oil pipe, and the rod cavities are interconnected through a oil pipe. Preferably, when the hydraulic cylinders on both sides rise, the motor 1 drives the hydraulic pump 2 to pump the hydraulic oil in the fuel tank 4 into the rodless cavities of all hydraulic cylinders. Further, the working volume in the rod cavities of all hydraulic cylinders decreases, causing some hydraulic oil to be extruded, flowing through the damping valve and servo valve and then returning to the inside of the fuel tank 4 through the second oil pipe. Preferably, when the hydraulic cylinders on both sides descend, the motor 1 drives the hydraulic pump 2 to pump the hydraulic oil in the fuel tank 4 into the rod cavities of all hydraulic cylinders. Further, the working volume in the rodless cavities of all hydraulic cylinders decreases, causing some hydraulic oil to be extruded, flowing through the damping valve and servo valve and then returning to the inside of the fuel tank 4 through the second oil pipe.

[0064] Preferably, as Figure 2 shown, for the single-axis module, all servo valves are in the left or right position, and the reversing valve is in the upper position, so that the single-axis module can form a cross-interconnected configuration in the first driving state. Preferably, when the single-axis module is in the cross-interconnected configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if it is desired to achieve forward roll control of the single-axis module, the left servo valve is in the left position and the right servo valve is in the right position; conversely, if it is desired to achieve reverse roll control of the single-axis module, the left servo valve is in the right position and the right servo valve is in the left position. At this time, the rodless cavity of the left hydraulic cylinder (i.e., the first hydraulic cylinder 11) is interconnected with the rod cavity of the right hydraulic cylinder (i.e., the second hydraulic cylinder 12) through a oil pipe, and the rod cavity of the left hydraulic cylinder (i.e., the first hydraulic cylinder 11) is interconnected with the rodless cavity of the right hydraulic cylinder (i.e., the second hydraulic cylinder 12) through a oil pipe.

[0065] Preferably, as Figure 2 shown, for the single-axis module, all the reversing valves are in the neutral position, and the servo valve works in the left or right position, so that the single-axis module can form an independent disconnection configuration in the first driving state. At this time, the single-axis module can be regarded as a combination of angular modules as Figure 6 shown. Preferably, when the single-axis module is in the independent disconnection configuration in the first driving state, the motor 1 and the hydraulic pump 2 pump oil into the oil pipe. Specifically, if the left (right) hydraulic cylinder is to be controlled to rise, the left (right) servo valve works in the left position; conversely, if the left (right) hydraulic cylinder is to be controlled to descend, the left (right) servo valve works in the right position. At this time, the rodless cavity and the rod cavity of a single hydraulic cylinder are independent of each other.

[0066] It should be noted that the above specific embodiments are exemplary. Those skilled in the art can come up with various solutions inspired by the disclosure of the present invention, and these solutions also fall within the disclosure scope and protection scope of the present invention. Those skilled in the art should understand that the description and drawings of the present invention are illustrative and do not constitute a limitation to the claims. The protection scope of the present invention is defined by the claims and their equivalents. The description of the present invention contains multiple inventive concepts. For example, "preferably" or "according to a preferred embodiment" indicates that an independent concept is disclosed in the corresponding paragraph. The applicant reserves the right to file divisional applications according to each inventive concept. Throughout the text, the features guided by "preferably" are only optional ways and should not be understood as must be provided. Therefore, the applicant reserves the right to abandon or delete relevant preferred features at any time.

Claims

1. A variable configuration suspension, characterized in that: It includes: One or more dual-axle modules including two axles and / or one or more single-axle modules including one axle, the dual-axle modules and the single-axle modules comprising: A plurality of hydraulic cylinders are provided with rodless chambers and rod chambers, and a connection circuit composed of oil pipes is used to connect or disconnect the rodless chambers and rod chambers of different hydraulic cylinders. The connection circuit includes: Multiple servo valves; one or more reversing valves; Several hydraulic branches and main hydraulic pipes, Among them, the first hydraulic branch pipe and the second hydraulic branch pipe are respectively connected to the rodless chamber and the rod chamber of the first hydraulic cylinder (11), the fifth hydraulic branch pipe and the sixth hydraulic branch pipe are respectively connected to the rodless chamber and the rod chamber of the third hydraulic cylinder (13), and the first reversing valve (41) is arranged at the connection between the first hydraulic branch pipe, the second hydraulic branch pipe, the fifth hydraulic branch pipe and the sixth hydraulic branch pipe to switch the connection state between the first hydraulic cylinder (11) and the third hydraulic cylinder (13) located on the same axle. The first hydraulic main pipe and the second hydraulic main pipe respectively connected to the first hydraulic branch pipe and the second hydraulic branch pipe are both connected to the first servo valve (51), and the fifth hydraulic main pipe and the sixth hydraulic main pipe respectively connected to the fifth hydraulic branch pipe and the sixth hydraulic branch pipe are connected to the third servo valve (53).

2. The variable configuration suspension according to claim 1, characterized in that: The servo valve and the reversing valve include three working positions. By switching the working positions, the four oil circuits connected to the servo valve and the reversing valve are switched between parallel interconnection, cross interconnection, and mutual disconnection.

3. The variable configuration suspension according to claim 2, characterized in that: For the dual-axis module, the reversing valve includes a third reversing valve (43) for switching the connection state between the second hydraulic cylinder (12) and the fourth hydraulic cylinder (14) located on the same axle, wherein the third hydraulic branch pipe and the fourth hydraulic branch pipe are respectively connected to the rodless chamber and the rod chamber of the second hydraulic cylinder (12), the seventh hydraulic branch pipe and the eighth hydraulic branch pipe are respectively connected to the rodless chamber and the rod chamber of the fourth hydraulic cylinder (14), and the third reversing valve (43) is arranged at the connection between the third hydraulic branch pipe, the fourth hydraulic branch pipe, the seventh hydraulic branch pipe and the eighth hydraulic branch pipe.

4. The variable configuration suspension according to claim 3, characterized in that: For the dual-axis module, the servo valve includes a second servo valve (52) and a fourth servo valve (54), wherein the third hydraulic main pipe and the fourth hydraulic main pipe respectively connected to the third hydraulic branch pipe and the fourth hydraulic branch pipe are both connected to the second servo valve (52), and the seventh hydraulic main pipe and the eighth hydraulic main pipe respectively connected to the seventh hydraulic branch pipe and the eighth hydraulic branch pipe are connected to the fourth servo valve (54).

5. The variable configuration suspension according to claim 4, characterized in that: For the dual-axis module, the reversing valve comprises a second reversing valve (42), and the second reversing valve (42) is connected to the first hydraulic main pipe, the second hydraulic main pipe, the third hydraulic main pipe, and the fourth hydraulic main pipe respectively through a first hydraulic bypass pipe, a second hydraulic bypass pipe, a third hydraulic bypass pipe, and a fourth hydraulic bypass pipe.

6. The variable configuration suspension according to claim 5, characterized in that: For a dual-axis module in the first drive state, Adjust each servo valve to the left or right position for operation, and adjust the reversing valve to the lower or middle position for operation, so that the dual-axis module switches to the parallel interconnection configuration in the first driving state; Adjust each servo valve to the left position or the right position for operation, and adjust the reversing valve to the upper position or the middle position for operation, so that the dual-axis module switches to the cross-connection configuration in the first driving state; Adjust each servo valve to the left or right position for operation, and adjust the reversing valve to the lower or middle position for operation, so that the dual-axis module switches to the pitch interconnected configuration in the first driving state; Each servo valve is adjusted to the left or right position for operation, and the reversing valve is adjusted to the middle position for operation, so that the dual-axis module is switched to the independent disconnection configuration in the first driving state, In the parallel interconnection configuration and the independent disconnection configuration, each servo valve is in the same working position; in the cross interconnection configuration, the first servo valve (51) and the second servo valve (52) are in the same working position and are opposite to the working position of the third servo valve (53) and the fourth servo valve (54); in the pitch interconnection configuration, the first servo valve (51) and the third servo valve (53) are in the same working position and are opposite to the working position of the second servo valve (52) and the fourth servo valve (54).

7. The variable configuration suspension according to claim 5, characterized in that: For a dual-axis module in the second drive state, Adjust each servo valve to a neutral position, and adjust the reversing valve to a lower position or a right position, so that the dual-axis module switches to a parallel interconnection configuration in a second driving state; Adjust each servo valve to a neutral position, and adjust the reversing valve to an upper position or a right position, so that the dual-axis module switches to a cross-connected configuration in a second driving state; Each servo valve is adjusted to the middle position for operation, and the reversing valve is adjusted to the lower position or the left position for operation, so that the dual-axis module switches to the pitch interconnection configuration in the second driving state.

8. The variable configuration suspension according to claim 2, characterized in that: For a single-axis module in the first drive state, Adjusting each servo valve to the left position or the right position for operation, and adjusting the first reversing valve (41) to the lower position for operation, so that the single-axis module switches to a parallel interconnected configuration in a first driving state; Adjusting each servo valve to the left position or the right position for operation, and adjusting the first reversing valve (41) to the upper position for operation, so that the single-axis module switches to the cross-connection configuration in the first driving state; Each servo valve is adjusted to the left or right position for operation, and the reversing valve is adjusted to the middle position for operation, so that the single-axis module is switched to the independent disconnection configuration in the first driving state, Wherein, in the parallel interconnection configuration and the independent disconnection configuration, each servo valve is in the same working position; in the cross-interconnection configuration, the working positions of the first servo valve (51) and the third servo valve (53) are opposite.

9. The variable configuration suspension according to claim 2, characterized in that: For a single-axis module in the second drive state, Adjusting each servo valve to a neutral position, and adjusting the first reversing valve (41) to a lower position, so that the single-axis module switches to a parallel interconnected configuration in a second driving state; Each servo valve is adjusted to work in the middle position, and the first reversing valve (41) is adjusted to work in the upper position, so that the single-axis module switches to the cross-connected configuration in the second driving state.

10. The variable configuration suspension according to claim 1 or 4, characterized in that: Each servo valve is connected to a corresponding hydraulic branch pipe through a hydraulic main pipe and is connected to a power source through an oil pipe at the other end thereof, wherein the power source comprises an oil tank (4), a filter (3), a hydraulic pump (2) and an electric motor (1); the electric motor (1) is capable of driving the hydraulic pump (2) to operate so as to drive the oil in the oil tank (4) to enter a first oil pipe equipped with a first check valve (29-a) through the filter (3); the refluxed oil enters the oil tank (4) through a second oil pipe equipped with a second check valve (29-b); and the two ends of the pressure limiting valve (5) are respectively connected to the first oil pipe and the second oil pipe.

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