Inflation and deflation system, oil-gas suspension system capable of automatically adjusting pressure, and pressure adjustment method

Abstract

The present invention belongs to the field of vehicle suspensions, and particularly relates to a gas charging and discharging system, an oil-gas suspension system capable of automatically adjusting pressure, and a pressure regulating method. The gas charging and discharging system includes a gas replenishing device, a first oil source mechanism, a second oil source mechanism, and a valve assembly. The gas replenishing device includes an oil chamber and a gas chamber. A first control valve is provided at the oil discharge port of the oil chamber of the gas replenishing device, and a second control valve and a third control valve connected in series are provided at the air vent of the gas chamber of the gas replenishing device. The oil output end of the first oil source mechanism is connected to the oil chamber of the gas replenishing device. The first output end of the valve assembly is connected to the third control valve, and the second output end of the valve assembly is respectively connected to the first control valve and the second control valve. The oil output end of the second oil source mechanism is connected to the input end of the valve assembly. The present invention solves the problem of insufficient compressible stroke of the double-chamber accumulator under heavy vehicle loads; by changing the stiffness characteristics of the oil-gas suspension under heavy vehicle loads, it solves the problem of excessive stiffness of the oil-gas suspension under heavy load conditions and improves the comfort of the vehicle.

Description

Technical Field

[0001] The present invention belongs to the field of vehicle suspensions, and particularly relates to a charging and discharging system, an oil-gas suspension system capable of automatically adjusting pressure, and a pressure regulating method. Background Art

[0002] The oil-gas suspension has non-linear damping characteristics and stiffness characteristics. It can ensure good shock absorption effect when the vehicle is lightly loaded, and can ensure vehicle stability when the vehicle is heavily loaded. It is widely used in the field of heavy-duty vehicles.

[0003] Common oil-gas suspensions usually have two forms of oil-gas springs. One is to directly charge gas into the hydraulic cylinder to form an oil-liquid mixing chamber in the cylinder. This method has the characteristic of small volume, but the corresponding bearing capacity is relatively low, and it is often used in the front suspension of vehicles. The other is to use the method of adding an accumulator outside the hydraulic cylinder, and the non-linear elastic force is provided by the compression of the gas in the accumulator. This structure requires an external accumulator, so it often needs to occupy a large installation volume, but the corresponding bearing capacity is also large, and it is often used in the rear suspension of vehicles.

[0004] Since the mass of a heavy-duty vehicle varies greatly between the no-load and heavy-load conditions, the pressure on the oil-gas spring under heavy load can reach 4-5 times that under light load, and the pressure change span is large. For the rear suspension, relying solely on the compression and expansion of a single gas cannot adapt to the working condition changes of the vehicle from no-load to heavy-load. Currently, a double-chamber accumulator with two different pressures is commonly used to solve this problem, that is, the low-pressure chamber works under the no-load (light-load) condition to ensure comfort, and the high-pressure chamber and the compressed low-pressure chamber work simultaneously under the full-load (heavy-load) condition to ensure the bearing pressure and stability.

[0005] When a fully loaded vehicle passes through a poor road surface, the peak value of the instantaneous impact force of the vehicle will increase sharply. This force will be transmitted to the double-chamber accumulator through the oil cylinder. When it exceeds the limit compression position of the low-pressure chamber, the piston of the low-pressure chamber will frequently hit the end cover of the accumulator. Long-term impact will damage the sealing effect of the accumulator, shortening the service life of the accumulator sharply. If the instantaneous impact is too large, it will directly cause the accumulator to be damaged, seriously affecting the safety of the vehicle. At the same time, limited by the installation space of the suspension, the volume of the double-chamber accumulator used for shock absorption is often small. And due to the design of the double-pressure chamber, the volume of the high-pressure chamber is further compressed, resulting in the fact that the double-chamber accumulator often cannot provide enough compressible space under heavy load. This will cause the stiffness of the oil cylinder to rise sharply when compressed to a certain extent, and then cause the oil cylinder to lose its shock absorption performance, reducing the comfort of the vehicle under heavy load conditions. Summary of the Invention

[0006] In order to overcome the deficiencies of the above-mentioned prior art, the present invention provides a charging and discharging system, an oil-gas suspension system capable of automatically adjusting pressure, and a pressure regulating method, which solve the problem of insufficient compressible stroke of the double-chamber accumulator when the vehicle is heavily loaded; by changing the stiffness characteristics of the oil-gas suspension when the vehicle is heavily loaded, solve the problem of excessive stiffness of the oil-gas suspension under heavy load conditions, and improve the comfort of the vehicle; in addition, it can also prevent the piston of the low-pressure air chamber from hitting the end cover of the double-chamber accumulator when the vehicle is heavily loaded on a poor road surface, and extend the service life of the double-chamber accumulator.

[0007] The present invention is realized through the following technical solutions: A charging and discharging system includes:

[0008] An air replenishing device, the air replenishing device includes an oil chamber and an air chamber. A first control valve is provided at the oil discharge port of the oil chamber of the air replenishing device, and a second control valve and a third control valve connected in series are provided at the air vent of the air chamber of the air replenishing device;

[0009] A first oil source mechanism, the oil output end of the first oil source mechanism is connected to the oil chamber of the air replenishing device. When the first oil source mechanism obtains a trigger signal, the first oil source mechanism delivers hydraulic oil to the oil chamber of the air replenishing device;

[0010] A valve assembly, the first output end of the valve assembly is connected to the third control valve, and the second output end of the valve assembly is respectively connected to the first control valve and the second control valve;

[0011] A second oil source mechanism, the oil output end of the second oil source mechanism is connected to the input end of the valve assembly. When the second oil source mechanism obtains a trigger signal, the second oil source mechanism delivers hydraulic oil to the input end of the valve assembly;

[0012] When the input end of the valve assembly is in communication with the first output end of the valve assembly, the hydraulic oil flowing out from the first output end of the valve assembly acts on the third control valve, so that the air vent of the air chamber of the air replenishing device can only be used for unidirectional gas output;

[0013] When the input end of the valve assembly is in communication with the second output end of the valve assembly, the hydraulic oil flowing out from the second output end of the valve assembly acts on the first control valve and the second control valve respectively, so that the oil discharge channel of the oil chamber of the air replenishing device via the oil discharge port is opened, and the air vent of the air chamber of the air replenishing device can only be used for unidirectional gas input.

[0014] In some embodiments, the first control valve, the second control valve, and the third control valve are all hydraulic check valves. The oil outlet of the first control valve is connected to the oil chamber of the air replenishing device, the air inlet of the second control valve is connected to the air chamber of the air replenishing device, and the air outlet of the third control valve is connected to the air outlet of the second control valve.

[0015] In some embodiments, the valve assembly includes a first reversing valve. The oil inlet of the first reversing valve is connected to the oil output end of the second oil source mechanism. The first working oil port of the first reversing valve is connected to a third control valve, and the second working oil port of the first reversing valve is respectively connected to a first control valve and a second control valve. The first reversing valve includes a first working position, a second working position, and a third working position.

[0016] When the first reversing valve is in the first working position, the oil inlet of the first reversing valve is communicated with the second working oil port of the first reversing valve.

[0017] When the first reversing valve is in the second working position, the oil inlet, the first working oil port, and the second working oil port of the first reversing valve are all in a cut-off state.

[0018] When the first reversing valve is in the third working position, the oil inlet of the first reversing valve is communicated with the first working oil port of the first reversing valve.

[0019] In some embodiments, the first reversing valve includes a first control end and a second control end.

[0020] When there is a control pressure input at the first control end, control the first reversing valve to be in the first working position.

[0021] When there is a control pressure input at the second control end, control the first reversing valve to be in the third working position.

[0022] When there is no control pressure input at both the first control end and the second control end, the first reversing valve is in the second working position.

[0023] In some embodiments, both the first oil source mechanism and the second oil source mechanism adopt mechanical oil pumps. The rodless cavity of the mechanical oil pump is the oil chamber. The mechanical oil pump is provided with an oil suction port and an oil output port. Both the oil suction port and the oil output port of the mechanical oil pump are communicated with the oil chamber of the mechanical oil pump, and both the oil suction port and the oil output port of the mechanical oil pump are unidirectionally conductive. An elastic element is arranged in the oil chamber of the mechanical oil pump. One end of the elastic element abuts against the piston of the mechanical oil pump, and the other end of the elastic element abuts against the inner side wall of the cylinder bottom of the mechanical oil pump.

[0024] The present invention also provides an automatically pressure-adjustable oil-gas suspension system, which includes a suspension cylinder installed on a vehicle, a double-chamber accumulator, an accumulator, and the above-mentioned air charging and discharging system.

[0025] The double-chamber accumulator includes a high-pressure gas chamber, a low-pressure gas chamber, and an oil chamber. The oil chamber of the double-chamber accumulator is located between the high-pressure gas chamber and the low-pressure gas chamber. The oil chamber of the double-chamber accumulator is separated from the high-pressure gas chamber and the low-pressure gas chamber by pistons respectively.

[0026] The rodless chamber of the suspension oil cylinder is the oil chamber, and the oil chamber of the suspension oil cylinder is connected to the oil chamber of the double-chamber accumulator;

[0027] The accumulator is arranged on the oil path between the oil output end of the second oil source mechanism in the air charging and discharging system and the input end of the valve assembly;

[0028] The air charging device in the air charging and discharging system is sequentially connected to the low-pressure air chamber of the double-chamber accumulator through a second control valve and a third control valve;

[0029] The telescopic movement of the piston rod of the suspension oil cylinder serves as a signal to trigger the action of the first oil source mechanism and the second oil source mechanism in the air charging and discharging system;

[0030] When the volume of the low-pressure air chamber of the double-chamber accumulator is in the minimum state, the valve assembly acts to make the input end of the valve assembly communicate with the first output end of the valve assembly;

[0031] When the volume of the low-pressure air chamber of the double-chamber accumulator is in the maximum state, the valve assembly acts to make the input end of the valve assembly communicate with the second output end of the valve assembly.

[0032] In some embodiments, the first control valve, the second control valve, and the third control valve in the air charging and discharging system are all pilot-operated check valves. The oil outlet of the first control valve is connected to the oil chamber of the air charging device, the air inlet of the second control valve is connected to the air chamber of the air charging device, and the air outlet of the third control valve is connected to the air outlet of the second control valve;

[0033] The valve assembly in the air charging and discharging system includes a first reversing valve. The oil inlet of the first reversing valve is connected to the oil output end of the second oil source mechanism. The first working oil port of the first reversing valve is connected to the control end of the third control valve. The second working oil port of the first reversing valve is respectively connected to the control end of the first control valve and the control end of the second control valve; The first reversing valve includes a first working position, a second working position, and a third working position;

[0034] When the first reversing valve is in the first working position, the oil inlet of the first reversing valve communicates with the second working oil port of the first reversing valve;

[0035] When the first reversing valve is in the second working position, the oil inlet, the first working oil port, and the second working oil port of the first reversing valve are all in a cut-off state;

[0036] When the first reversing valve is in the third working position, the oil inlet of the first reversing valve communicates with the first working oil port of the first reversing valve.

[0037] In some embodiments, the first reversing valve includes a first control end and a second control end;

[0038] When there is a control pressure input at the first control end, control the first reversing valve to be in the first working position;

[0039] When there is a control pressure input at the second control end, control the first reversing valve to be in the third working position;

[0040] When there is no control pressure input at both the first control end and the second control end, the first reversing valve is in the second working position;

[0041] The valve assembly further includes a second reversing valve and a third reversing valve;

[0042] The oil inlet of the second reversing valve is connected to the oil output end of the second oil source mechanism, the working oil port of the second reversing valve is connected to the first control end of the first reversing valve, and the oil return port of the second reversing valve is connected to the oil tank; the second reversing valve includes a first working position and a second working position;

[0043] When the second reversing valve is in the first working position, the working oil port of the second reversing valve is connected to the oil inlet of the second reversing valve;

[0044] When the second reversing valve is in the second working position, the working oil port of the second reversing valve is connected to the oil return port of the second reversing valve;

[0045] The oil inlet of the third reversing valve is connected to the oil output end of the second oil source mechanism, the working oil port of the third reversing valve is connected to the second control end of the first reversing valve, and the oil return port of the third reversing valve is connected to the oil tank; the third reversing valve includes a first working position and a second working position;

[0046] When the third reversing valve is in the first working position, the working oil port of the third reversing valve is connected to the oil inlet of the third reversing valve;

[0047] When the third reversing valve is in the second working position, the working oil port of the third reversing valve is connected to the oil return port of the third reversing valve.

[0048] In some embodiments, the second reversing valve includes a first control end and a second control end;

[0049] A valve core is provided at the first control end of the second reversing valve. The valve core is placed in the hydraulic cavity of the double-chamber energy accumulator. The valve core at the first control end of the second reversing valve is controlled by the piston in the low-pressure gas cavity of the double-chamber energy accumulator. The first control end of the second reversing valve is used to control the second reversing valve to be in the first working position;

[0050] A spring is provided at the second control end of the second reversing valve for controlling the second reversing valve to be in the second working position;

[0051] The third reversing valve includes a first control end and a second control end;

[0052] A spool is provided at the first control end of the third reversing valve. The spool is placed in the low-pressure air chamber of the double-chamber accumulator. The spool at the first control end of the third reversing valve is controlled by the piston in the low-pressure air chamber of the double-chamber accumulator. The first control end of the third reversing valve is used to control the third reversing valve to be in the first working position;

[0053] A spring is provided at the second control end of the third reversing valve for controlling the third reversing valve to be in the second working position.

[0054] In some embodiments, a damping hole is provided on the oil path where the working oil port of the second reversing valve is connected to the first control end of the first reversing valve; a damping hole is provided on the oil path where the working oil port of the third reversing valve is connected to the second control end of the first reversing valve.

[0055] In some embodiments, both the first oil source mechanism and the second oil source mechanism adopt mechanical oil pumps. The rodless chamber of the mechanical oil pump is the oil chamber. The mechanical oil pump is provided with an oil suction port and an oil output port. Both the oil suction port and the oil output port of the mechanical oil pump are communicated with the oil chamber of the mechanical oil pump, and both the oil suction port and the oil output port of the mechanical oil pump are unidirectionally conductive; an elastic element is provided in the oil chamber of the mechanical oil pump. One end of the elastic element abuts against the piston of the mechanical oil pump, and the other end of the elastic element abuts against the inner side wall of the bottom of the cylinder of the mechanical oil pump;

[0056] Both the first oil source mechanism and the second oil source mechanism are provided on the cylinder block of the suspension cylinder, and the first oil source mechanism and the second oil source mechanism are respectively located on both sides of the suspension cylinder. An impact plate is provided on the piston rod of the suspension cylinder. The pump rods of both the first oil source mechanism and the second oil source mechanism are on the movement track of the impact plate, and the distance between the pump rod of the first oil source mechanism and the impact plate is equal to the distance between the pump rod of the second oil source mechanism and the impact plate.

[0057] The present invention also provides a pressure regulating method, including the above-mentioned automatically pressure-regulating oil-gas suspension system;

[0058] When the vehicle is lightly loaded, the impact plate does not touch the pump rods of both the first oil source mechanism and the second oil source mechanism, and neither the first oil source mechanism nor the second oil source mechanism obtains a trigger signal;

[0059] When the vehicle is heavily loaded, the piston rod of the suspension cylinder is compressed and moves a certain distance into the suspension cylinder. When the vehicle passes through a bumpy road surface, the piston rod of the suspension cylinder drives the impact plate to vibrate up and down repeatedly, so that the impact plate repeatedly hits the pump rods of the first oil source mechanism and the second oil source mechanism. The pump rods of the first oil source mechanism and the second oil source mechanism perform reciprocating telescopic actions. In addition, when the piston rod of the suspension cylinder retracts, it will press the hydraulic oil in the oil chamber of the suspension cylinder into the oil chamber of the double-chamber accumulator;

[0060] When the pump rod of the first oil source mechanism retracts under the impact force provided by the impact plate, the oil chamber of the first oil source mechanism delivers hydraulic oil to the oil chamber of the air replenishing device through the output oil port. When the pump rod of the first oil source mechanism extends under the elastic force provided by the elastic element, the oil chamber of the first oil source mechanism replenishes hydraulic oil through the oil suction port; the oil chamber of the air replenishing device pushes the piston to compress the air chamber of the air replenishing device under the action of the hydraulic oil provided by the first oil source mechanism;

[0061] When the pump rod of the second oil source mechanism retracts under the impact force provided by the impact plate, the oil chamber of the second oil source mechanism delivers hydraulic oil to the input end of the valve assembly through the output oil port. When the pump rod of the second oil source mechanism extends under the elastic force provided by the elastic element, the oil chamber of the second oil source mechanism replenishes hydraulic oil through the oil suction port;

[0062] When the piston of the low-pressure air chamber of the double-chamber accumulator squeezes the volume of the low-pressure air chamber of the double-chamber accumulator into the smallest state, the input end of the valve assembly is in communication with the first output end of the valve assembly. The hydraulic oil flowing out from the first output end of the valve assembly acts on the third control valve, so that the air vent of the air chamber of the air replenishing device can only be used for unidirectional gas output. The compressed high-pressure gas in the air chamber of the air replenishing device flows to the low-pressure air chamber of the double-chamber accumulator, realizing the pressurization of the low-pressure air chamber of the double-chamber accumulator;

[0063] When the vehicle unloads, the piston of the low-pressure air chamber of the double-chamber accumulator resets, and the volume of the low-pressure air chamber of the double-chamber accumulator is in the largest state. The input end of the valve assembly is in communication with the second output end of the valve assembly. The hydraulic oil flowing out from the second output end of the valve assembly acts on the first control valve and the second control valve respectively. At this time, the first control valve opens the oil discharge channel of the oil chamber of the air replenishing device via the oil discharge port, and the piston of the air replenishing device moves, so that the air chamber of the air replenishing device increases, and the gas pressure in the air chamber of the air replenishing device decreases. In addition, the second control valve makes the air vent of the air chamber of the air replenishing device can only be used for unidirectional gas input, and the high-pressure gas in the low-pressure air chamber of the double-chamber accumulator flows back to the air chamber of the air replenishing device.

[0064] The beneficial effects of the present invention are as follows: The oil-gas suspension system that can automatically adjust the pressure composed of the air charging and discharging system is used to adjust the pressure of the low-pressure air chamber of the double-chamber accumulator. When the vehicle is heavily loaded and receives a large impact, the low-pressure air chamber of the double-chamber accumulator is pressurized, avoiding the impact of the low-pressure piston on the end cover of the low-pressure cylinder barrel and improving the service life of the double-chamber accumulator. At the same time, because the high-pressure air chamber of the double-chamber accumulator will work only when the pressure of the low-pressure air chamber of the double-chamber accumulator is the same as that of the high-pressure air chamber of the double-chamber accumulator, pressurizing the low-pressure air chamber of the double-chamber accumulator also enables the high-pressure air chamber of the double-chamber accumulator to provide sufficient compressible space. Compared with the existing vehicle suspension, it ensures that the vehicle has good comfort under both light and heavy load conditions and improves the safety of the vehicle under heavy load conditions.

[0065] The control valve adopted by the oil-gas suspension system is integrated into the large components of the system, requiring less installation space. Brief Description of the Drawings

[0066] Figure 1 is the hydraulic schematic diagram of the present invention;

[0067] Figure 2 is the structural schematic diagram of the air charging device of the present invention;

[0068] Figure 3 is the structural schematic diagram of the first oil source mechanism of the present invention;

[0069] Figure 4 is the structural schematic diagram of the first reversing valve of the present invention;

[0070] Figure 5 is the structural schematic diagram of the double-chamber accumulator of the present invention;

[0071] Figure 6 is the structural schematic diagram of the second reversing valve of the present invention;

[0072] In the figure, 1 is the air charging device, 11 is the first control valve, 111 is the annular sleeve, 112 is the push rod, 113 is the first valve core, 114 is the first spring, 115 is the bolt, 12 is the second control valve, 13 is the third control valve, 14 is the first cylinder barrel, 15 is the first piston, 16 is the upper end cover, 17 is the lower end cover, 171 is the guiding hole, 2 is the first oil source mechanism, 21 is the second cylinder barrel, 22 is the second piston, 23 is the pump rod, 24 is the first check valve, 25 is the second check valve, 26 is the second spring, 3 is the valve assembly, 31 is the first reversing valve, 311 is the conical valve, 312 is the second valve core, 313 is the first valve body, 314 is the third spring, 315 is the first valve cover, 316 is the control end oil passage, 32 is the second reversing valve, 321 is the second valve body, 322 is the second valve cover, 323 is the third valve core, 324 is the fourth spring, 33 is the third reversing valve, 4 is the second oil source mechanism, 5 is the suspension oil cylinder, 51 is the impact plate, 6 is the double-chamber accumulator, 61 is the low-pressure cylinder barrel, 62 is the high-pressure cylinder barrel, 63 is the connecting annular sleeve, 64 is the low-pressure piston, 65 is the high-pressure piston, 7 is the accumulator, 8 is the first relief valve, and 9 is the second relief valve. Detailed Embodiments

[0073] The present invention will be further described below with reference to the drawings and embodiments.

[0074] As Figure 1 shown, a gas charging and discharging system includes an air charging device 1, a first oil source mechanism 2, a valve assembly 3, and a second oil source mechanism 4.

[0075] The air replenishing device 1 includes an oil chamber and an air chamber, and the oil chamber and the air chamber of the air replenishing device 1 are separated by a piston; an oil discharge port of the oil chamber of the air replenishing device 1 is provided with a first control valve 11, and an air vent of the air chamber of the air replenishing device 1 is provided with a second control valve 12 and a third control valve 13 connected in series. In some embodiments, the first control valve 11, the second control valve 12, and the third control valve 13 are all pilot-operated check valves. An oil outlet of the first control valve 11 is connected to the oil chamber of the air replenishing device 1, an air inlet of the second control valve 12 is connected to the air chamber of the air replenishing device 1, and an air outlet of the third control valve 13 is connected to an air outlet of the second control valve 12.

[0076] The specific structure of the air replenishing device 1 is as Figure 2 shown, and it includes a first cylinder barrel 14 and a first piston 15 arranged in the first cylinder barrel 14. Both ends of the first cylinder barrel 14 are of an open structure, and an upper end cover 16 and a lower end cover 17 are respectively arranged at the openings at both ends of the first cylinder barrel 14. A cavity between the upper end cover 16 and the first piston 15 of the first cylinder barrel 14 is the air chamber of the air replenishing device 1, and a cavity between the lower end cover 17 and the first piston 15 of the first cylinder barrel 14 is the oil chamber of the air replenishing device 1. Among them, a second control valve 12 and a third control valve 13 connected in series are integrated in the upper end cover 16, and a first control valve 11 is integrated in the lower end cover 17. Specifically, the basic structures of the second control valve 12 integrated in the upper end cover 16 and the third control valve 13 integrated in the upper end cover 16 are the same as the basic structure of the first control valve 11 integrated in the lower end cover 17. Now, taking the integration of the first control valve 11 in the lower end cover 17 as an example, how to integrate the control valve in the end cover will be described. As Figure 2As shown, the lower end cover 17 serves as the valve body of the first control valve 11. A guide hole 171 is provided through the lower end cover 17. A bolt 115 is connected to one end of the guide hole 171, and an annular sleeve 111 is connected to the other end of the guide hole 171. A first valve core 113 and a push rod 112 are provided between the bolt 115 and the annular sleeve 111. The first valve core 113 is fixedly connected to the push rod 112. A first spring 114 is provided between the bolt 115 and the end of the first valve core 113 away from the push rod 112. The first valve core 113 can move left and right within the guide hole 171. The leftward movement of the first valve core 113 is restricted by the bolt 115, and the rightward movement of the first valve core 113 is restricted by the shoulder on the guide hole 171. An oil outlet passage (i.e., the oil outlet of the first control valve 11) and an oil inlet passage (i.e., the oil inlet of the first control valve 11) are provided on the lower end cover 17. Both the oil outlet passage and the oil inlet passage are connected to the guide hole 171. The oil outlet passage on the lower end cover 17 is connected to the oil chamber of the air replenishment device 1, and the oil inlet passage is located between the first valve core 113 and the push rod 112. Initially, under the action of the first spring 114, the inclined surface of the first valve core 113 is in close contact with the shoulder of the guide hole 171, and the first valve core 113 closes the oil outlet passage, thus isolating the oil inlet and outlet passages. When the first control valve 11 flows in the forward direction, oil is supplied from the oil inlet channel, and the hydraulic oil enters between the valve core 113 and the push rod 112, pushing the valve core 113 to the left while overcoming the elastic force provided by the first spring 114. The oil outlet channel on the lower end cover 17 is opened, and the oil inlet channel and the oil outlet channel on the lower end cover 17 are connected. After the oil inlet channel stops supplying oil, the oil outlet channel is closed again under the action of the first spring 114. When reverse flow is required in the first control valve 11, control oil is introduced into the annular sleeve 111 (i.e., the control end of the first control valve 11). The hydraulic oil, overcoming the elastic force provided by the first spring 114, pushes the push rod 112, which in turn drives the valve core 113 to the left. The oil outlet passage on the lower end cover 17 is opened, and the oil inlet and outlet passages on the lower end cover 17 are connected. At this point, the hydraulic oil in the oil chamber of the air replenishing device 1 can flow out toward the oil inlet passage through the oil outlet passage on the lower end cover 17. After the control oil is no longer introduced into the annular sleeve 111, the oil outlet passage is again closed under the action of the first spring 114. The basic structures of the second control valve 12 and the third control valve 13 integrated within the upper end cover 16 are similar to the above-described structure of the first control valve 11 integrated within the lower end cover 17. The second and third control valves 12, 13 are connected in series. Specifically, the oil outlet of the second control valve 12 is connected to the oil outlet of the third control valve 13. The present application is not limited to the structural form in which the first control valve 11, the second control valve 12 and the third control valve 13 are integrated in the corresponding end covers, and an external form can also be adopted, that is, the hydraulically controlled one-way valve is connected to the air supply device 1 with a connecting pipe.

[0077] The oil delivery end of the first oil source mechanism 2 is connected to the oil chamber of the air supplement device 1. When the first oil source mechanism 2 obtains a trigger signal, the first oil source mechanism 2 delivers hydraulic oil to the oil chamber of the air supplement device 1. The first oil source mechanism 2 uses a mechanical oil pump, and the specific structure of the first oil source mechanism 2 is as Figure 3 shown, including a second cylinder 21 and a second piston 22 disposed within the second cylinder 21. The second piston 22 is fixedly connected to the pump rod 23, and the second piston 22 can move up and down along the inner cavity of the second cylinder 21. The inner cavity of the second cylinder 21 on the side without the pump rod 23 is the oil chamber. The bottom of the second cylinder 21 is provided with an oil suction port and an oil output port, and both the oil suction port and the oil output port are communicated with the oil chamber of the second cylinder 21. An internal check valve one 24 is provided in the oil suction port, and the check valve one 24 conducts unidirectionally from the outside of the second cylinder 21 towards the oil chamber of the second cylinder 21. An internal check valve two 25 is provided in the oil output port, and the check valve two 25 conducts unidirectionally from the oil chamber of the second cylinder 21 towards the outside of the second cylinder 21. A second spring 26 is disposed in the oil chamber of the second cylinder 21. One end of the second spring 26 abuts against the second piston 22, and the other end of the second spring 26 abuts against the inner side wall of the bottom of the second cylinder 21. During use, the oil suction port of the second cylinder 21 is externally connected to a fuel tank, and the oil output port of the second cylinder 21 is connected to the oil chamber of the air supplement device 1. When the second piston 22 is retracted under the external force transmitted from the pump rod 23 to overcome the elastic force provided by the second spring 26 and squeeze the oil chamber of the second cylinder 21, the hydraulic oil in the oil chamber of the second cylinder 21 flows out from the check valve two 25 and flows towards the oil chamber of the air supplement device 1; when the external force provided by the pump rod 23 is lost and the second piston 22 extends under the action of the second spring 26, the oil chamber of the second cylinder 21 sucks oil from the fuel tank through the check valve one 24. The second piston 22 repeatedly makes telescopic movements, and thus can continuously deliver hydraulic oil to the oil chamber of the air supplement device 1. This application is not limited to the above structural form in which the internal check valve one 24 is provided in the oil suction port and the internal check valve two 25 is provided in the oil output port, and an external form can also be adopted, that is, the external check valve one 24 is connected to the oil suction port of the second cylinder 21 with a connecting pipe, and the external check valve two 25 is connected to the oil output port of the second cylinder 21 with a connecting pipe.

[0078] The first output end of the valve assembly 3 is connected to the control end of the third control valve 13, and the second output end of the valve assembly 3 is respectively connected to the control ends of the first control valve 11 and the second control valve 12. In some embodiments, the valve assembly 3 includes a first reversing valve 31, and the first reversing valve 31 is a three-position three-way valve. The oil inlet of the first reversing valve 31 is connected to the oil output end of the second oil source mechanism 4. The first working oil port of the first reversing valve 31 (i.e., the first output end of the valve assembly 3) is connected to the control end of the third control valve 13, and the second working oil port of the first reversing valve 31 (i.e., the second output end of the valve assembly 3) is respectively connected to the control ends of the first control valve 11 and the second control valve 12. The first reversing valve 31 includes a first working position, a second working position and a third working position. The structural form of the second oil source mechanism 4 is the same as that of the first oil source mechanism 2, and will not be described in detail here.

[0079] When the first reversing valve 31 is in the first working position, the oil inlet of the first reversing valve 31 is communicated with the second working oil port of the first reversing valve 31. At this time, the hydraulic oil at the oil inlet of the first reversing valve 31 will act on the control ends of the first control valve 11 and the second control valve 12 through the second working oil port of the first reversing valve 31, so that both the first control valve 11 and the second control valve 12 are opened for reverse flow. The hydraulic oil in the oil chamber of the air replenishing device 1 can flow back to the fuel tank through the first control valve 11, realizing the oil discharge of the oil chamber of the air replenishing device 1. At the same time, with the oil discharge of the oil chamber of the air replenishing device 1, the pressure in the oil chamber of the air replenishing device 1 decreases, the air pressure in the air chamber of the air replenishing device 1 is greater than the oil pressure in the oil chamber of the air replenishing device 1, and the first piston 15 in the first cylinder barrel 14 moves towards the oil chamber of the air replenishing device 1, the volume of the air chamber of the air replenishing device 1 increases, and the air pressure in the air chamber of the air replenishing device 1 will decrease accordingly; and the reverse opening of the second control valve 12 forms a one-way conducting air path from the third control valve 13 through the second control valve 12 to the air chamber of the air replenishing device 1, and the external air source can inflate the air chamber of the air replenishing device 1.

[0080] When the first reversing valve 31 is in the second working position, the oil inlet of the first reversing valve 31, the first working oil port of the first reversing valve 31 and the second working oil port of the first reversing valve 31 are all in a cut-off state. The first working oil port and the second working oil port of the first reversing valve 31 do not receive hydraulic oil, and the first control valve 11, the second control valve 12 and the third control valve 13 are in the initial one-way conducting state.

[0081] When the first reversing valve 31 is in the third working position, the oil inlet of the first reversing valve 31 is communicated with the first working oil port of the first reversing valve 31. At this time, the hydraulic oil at the oil inlet of the first reversing valve 31 will act on the control end of the third control valve 13 via the first working oil port of the first reversing valve 31, and the third control valve 13 opens for reverse flow. A one-way conduction gas path is formed from the gas cavity of the air supplement device 1 through the second control valve 12 to the third control valve 13. At this time, with the first oil source mechanism 2 supplying oil to the oil cavity of the air supplement device 1, the high-pressure gas in the gas cavity of the air supplement device 1 can output gas to the outside.

[0082] In some embodiments, the first reversing valve 31 includes a first control end and a second control end.

[0083] When a control pressure is input at the first control end, control the first reversing valve 31 to be in the first working position, and the oil inlet of the first reversing valve 31 is communicated with the second working oil port of the first reversing valve 31.

[0084] When a control pressure is input at the second control end, control the first reversing valve 31 to be in the third working position, and the oil inlet of the first reversing valve 31 is communicated with the first working oil port of the first reversing valve 31.

[0085] When there is no control pressure input at both the first control end and the second control end, the first reversing valve 31 is in the second working position, and the oil inlet, the first working oil port and the second working oil port of the first reversing valve 31 are all in a cut-off state.

[0086] The specific structure of the first reversing valve 31 is as Figure 4 shown, including a first valve body 313. First valve covers 315 are symmetrically arranged on both sides of the first valve body 313. The first valve body 313 is provided with a through guiding hole for placing a second valve core 312. The second valve core 312 can move left and right in the first valve body 313. Third springs 314 are arranged on both sides of the second valve core 312, and the other ends of the third springs 314 are in contact with the first valve covers 315. The first valve covers 315 are provided with control end oil channels 316 communicated with the guiding holes of the first valve body 313. As Figure 4As shown in the figure, the first working oil port of the first reversing valve 31, the oil inlet of the first reversing valve 31, and the second working oil port of the first reversing valve 31 are sequentially arranged on the first valve body 313 from left to right; the control end oil passage 316 located on the left side of the first valve body 313 is a part of the first control end of the first reversing valve 31, and the control end oil passage 316 located on the right side of the first valve body 313 is a part of the second control end of the first reversing valve 31. In the initial state, there is no control oil in the control end oil passage 316 of the first control end and the control end oil passage 316 of the second control end. The second spool 312 is in the middle position under the control of the third springs 314 on both sides, that is, the first reversing valve 31 is in the second working position. When control oil is introduced into the control end oil passage 316 of the first control end, the second spool 312 moves to the right against the elastic force provided by the third spring 314 on the right side, so that the oil inlet of the first reversing valve 31 and the second working oil port of the first reversing valve 31 are conducted, and the first reversing valve 31 is in the first working position; after the control oil supply to the control end oil passage 316 of the first control end stops, under the action of the third spring 314 on the right side, the second spool 312 returns to the middle position. When control oil is introduced into the control end oil passage 316 of the second control end, the second spool 312 moves to the left against the elastic force provided by the third spring 314 on the left side, so that the oil inlet of the first reversing valve 31 and the first working oil port of the first reversing valve 31 are conducted, and the first reversing valve 31 is in the third working position; after the control oil supply to the control end oil passage 316 of the second control end stops, under the action of the third spring 314 on the left side, the second spool 312 returns to the middle position.

[0087] In some embodiments, as Figure 4 shown, a poppet valve 311 is further provided on the first valve cover 315, and the poppet valve 311 is threadedly connected to the first valve cover 315. By changing the screwing depth of the poppet valve 311, the opening degree of the control end oil passage 316 is adjusted, and the poppet valve 311 plays a role in adjusting the damping of the damping hole in the hydraulic system.

[0088] Based on the above charging and discharging air system, the present invention further provides an automatically adjustable oil-gas suspension system, including a suspension cylinder 5, a double-chamber accumulator 6, an accumulator 7, and the above charging and discharging air system installed on a vehicle.

[0089] The double-chamber accumulator 6 includes a high-pressure gas chamber, a low-pressure gas chamber, and an oil chamber. The oil chamber of the double-chamber accumulator 6 is located between the high-pressure gas chamber and the low-pressure gas chamber, and the oil chamber of the double-chamber accumulator 6 is separated from the high-pressure gas chamber and the oil chamber of the double-chamber accumulator 6 is separated from the low-pressure gas chamber by pistons respectively. The specific structure of the double-chamber accumulator 6 is as Figure 5As shown in the figure, it includes a low-pressure cylinder barrel 61 and a high-pressure cylinder barrel 62. The low-pressure cylinder barrel 61 and the high-pressure cylinder barrel 62 are connected as a whole through a connecting annular sleeve 63. A movable low-pressure piston 64 is arranged in the low-pressure cylinder barrel 61, and a movable high-pressure piston 65 is arranged in the high-pressure cylinder barrel 62. The cavity between the low-pressure piston 64 and the high-pressure piston 65 is the oil chamber of the double-chamber accumulator 6. The side of the low-pressure piston 64 away from the high-pressure piston 65 is the low-pressure gas chamber of the double-chamber accumulator 6, and the side of the high-pressure piston 65 away from the low-pressure piston 64 is the high-pressure gas chamber of the double-chamber accumulator 6. Two openings communicating with the oil chamber of the double-chamber accumulator 6 are arranged on the connecting annular sleeve 63, and the two openings on the connecting annular sleeve 63 are used to connect with the suspension cylinders 5 on the left and right sides of the vehicle. The air replenishing device 1 in the air charging and discharging system is connected to the low-pressure gas chamber of the double-chamber accumulator 6 through a second control valve 12 and a third control valve 13 in sequence. The rodless chamber of the suspension cylinder 5 is the oil chamber, and the oil chamber of the suspension cylinder 5 is connected to the oil chamber of the double-chamber accumulator 6.

[0090] The accumulator 7 is arranged on the oil path between the oil output end of the second oil source mechanism 4 and the input end of the valve assembly 3 in the air charging and discharging system, and a second overflow valve 9 is also arranged on the oil path between the oil output end of the second oil source mechanism 4 and the input end of the valve assembly 3. When the system hydraulic pressure of the valve assembly 3 is relatively high, the high-pressure hydraulic oil can overflow through the second overflow valve 9, thereby protecting the valve assembly 3. In addition, a first overflow valve 8 that plays an overflow role is also arranged on the oil path between the oil output end of the first oil source mechanism 2 and the air replenishing device 1.

[0091] As Figure 1As shown in the figure, both the first oil source mechanism 2 and the second oil source mechanism 4 are arranged on the cylinder block of the suspension cylinder 5, and the first oil source mechanism 2 and the second oil source mechanism 4 are respectively located on both sides of the suspension cylinder 5. An impact plate 51 is arranged on the piston rod of the suspension cylinder 5. The pump rods of the first oil source mechanism 2 and the second oil source mechanism 4 are both on the movement track of the impact plate 51, and the distance between the pump rod of the first oil source mechanism 2 and the impact plate 51 is equal to the distance between the pump rod of the second oil source mechanism 4 and the impact plate 51. The telescopic movement of the piston rod of the suspension cylinder 5 will drive the impact plate 51 to move reciprocally, and the reciprocal movement of the impact plate 51 serves as a signal to trigger the actions of the first oil source mechanism 2 and the second oil source mechanism 4. When the impact plate 51 impacts the pump rods of the first oil source mechanism 2 and the second oil source mechanism 4, the first oil source mechanism 2 delivers hydraulic oil to the oil chamber of the air replenishing device 1, and the second oil source mechanism 4 delivers hydraulic oil to the valve assembly 3. When the impact plate 51 moves in the direction away from the pump rods of the first oil source mechanism 2 and the second oil source mechanism 4, the first oil source mechanism 2 starts to suck oil from the fuel tank into the oil chambers of the air replenishing device 1 and the second oil source mechanism 4. When the piston rod of the suspension cylinder 5 retracts, the hydraulic oil in the oil chamber of the suspension cylinder 5 will also be pressed into the oil chamber of the double-chamber accumulator 6. This process is that the double-chamber accumulator 6 absorbs the impact force transmitted by the suspension cylinder 5 to ensure the stable operation of the vehicle.

[0092] The valve assembly 3 further includes a second reversing valve 32 and a third reversing valve 33; the second reversing valve 32 is used to control the first control end of the first reversing valve 31, and the third reversing valve 33 is used to control the second control end of the first reversing valve 31.

[0093] The oil inlet of the second reversing valve 32 is connected to the oil output end of the second oil source mechanism 4, the working oil port of the second reversing valve 32 is connected to the first control end of the first reversing valve 31, and the oil return port of the second reversing valve 32 is connected to the fuel tank. The second reversing valve 32 includes a first working position and a second working position (as Figure 1 shown, the left side of the second reversing valve 32 is the first working position, and the right side of the second reversing valve 32 is the second working position).

[0094] When the second reversing valve 32 is in the first working position, the working oil port of the second reversing valve 32 is connected to the oil inlet of the second reversing valve 32; at this time, if the second oil source mechanism 4 provides hydraulic oil, it will flow from the oil inlet of the second reversing valve 32 through the working oil port of the second reversing valve 32 to the first control end of the first reversing valve 31, and switch the first reversing valve 31 to the first working position.

[0095] When the second reversing valve 32 is in the second working position, the working oil port of the second reversing valve 32 is connected to the oil return port of the second reversing valve 32; there is no control oil acting on the first control end of the first reversing valve 31.

[0096] In some embodiments, the second reversing valve 32 includes a first control end and a second control end. The second reversing valve 32 controls the switching between the first working position and the second working position through its first control end and second control end.

[0097] A valve core is provided at the first control end of the second reversing valve 32. The valve core is placed in the hydraulic cavity of the double-chamber accumulator 6. The valve core at the first control end of the second reversing valve 32 is controlled by the piston in the low-pressure gas cavity of the double-chamber accumulator 6. The first control end of the second reversing valve 32 is used to control the second reversing valve 32 to be in the first working position.

[0098] A spring is provided at the second control end of the second reversing valve 32 for controlling the second reversing valve 32 to be in the second working position.

[0099] The specific structure of the second reversing valve 32 is as Figure 6 shown, including a second valve body 321 and a second valve cover 322 provided on one side of the second valve body 321. The second valve cover 322 is fixed to the second valve body 321 by bolts. A guiding hole for installing a third valve core 323 is provided in the second valve body 321. The third valve core 323 can slide left and right in the second valve body 321. A fourth spring 324 is further provided between the third valve core 323 and the second valve cover 322. One end of the third valve core 323 away from the fourth spring 324 extends out of the second valve body 321. As Figure 6 shown, the oil inlet of the second reversing valve 32, the working oil port of the second reversing valve 32, and the oil return port of the second reversing valve 32 are sequentially arranged from left to right on the second valve body 321; in the initial state, under the elastic force provided by the fourth spring 324, the third valve core 323 makes the working oil port of the second reversing valve 32 communicate with the oil return port of the second reversing valve 32; when the third valve core 323 is acted on by an external force to overcome the elastic force provided by the fourth spring 324 and moves leftward, the working oil port of the second reversing valve 32 communicates with the oil inlet of the second reversing valve 32.

[0100] The oil inlet of the third reversing valve 33 is connected to the oil output end of the second oil source mechanism 4. The working oil port of the third reversing valve 33 is connected to the second control end of the first reversing valve 31. The oil return port of the third reversing valve 33 is connected to the fuel tank; the third reversing valve 33 includes a first working position and a second working position (as Figure 1 shown, the left side of the third reversing valve 33 is the second working position, and the right side of the third reversing valve 33 is the first working position).

[0101] When the third reversing valve 33 is in the first working position, the working oil port of the third reversing valve 33 is connected to the oil inlet of the third reversing valve 33; at this time, if the second oil source mechanism 4 provides hydraulic oil, it will flow from the oil inlet of the third reversing valve 33 through the working oil port of the third reversing valve 33 to the second control end of the first reversing valve 31, and switch the first reversing valve 31 to the third working position.

[0102] When the third reversing valve 33 is in the second working position, the working oil port of the third reversing valve 33 is connected to the oil return port of the third reversing valve 33; there is no control oil acting on the second control end of the first reversing valve 31.

[0103] The third reversing valve 33 includes a first control end and a second control end, and the third reversing valve 33 controls the switching of the working positions through its first control end and second control end.

[0104] A valve core is provided at the first control end of the third reversing valve 33. The valve core is placed in the low-pressure gas chamber of the double-chamber accumulator 6. The valve core at the first control end of the third reversing valve 33 is controlled by the piston in the low-pressure gas chamber of the double-chamber accumulator 6. The first control end of the third reversing valve 33 is used to control the third reversing valve 33 to be in the first working position.

[0105] A spring is provided at the second control end of the third reversing valve 33 for controlling the third reversing valve 33 to be in the second working position.

[0106] The basic structure of the third reversing valve 33 is the same as that of the second reversing valve 32, that is, the structure as Figure 6 shown, and the specific structure of the third reversing valve 33 will not be elaborated here.

[0107] For the structural arrangement in which the valve core at the first control end of the second reversing valve 32 is controlled by the low-pressure piston 64 in the low-pressure gas chamber of the double-chamber accumulator 6 and the structural arrangement in which the valve core at the first control end of the third reversing valve 33 is controlled by the low-pressure piston 64 in the low-pressure gas chamber of the double-chamber accumulator 6, refer to Figure 5 . The second reversing valve 32 is arranged in the oil chamber of the double-chamber accumulator 6, and the valve core of the second reversing valve 32 faces the low-pressure piston 64; the third reversing valve 33 is arranged outside the double-chamber accumulator 6, and the valve core of the third reversing valve 33 extends into the low-pressure gas chamber of the double-chamber accumulator 6. When the volume of the low-pressure gas chamber of the double-chamber accumulator 6 is in the maximum state, the low-pressure piston 64 presses the valve core of the second reversing valve 32, making the second reversing valve 32 in the first working position; when the volume of the low-pressure gas chamber of the double-chamber accumulator 6 is in the minimum state, the low-pressure piston 64 presses the valve core of the third reversing valve 33, making the third reversing valve 33 in the first working position.

[0108] The present invention also provides a pressure regulating method, including the above-mentioned automatically pressure-regulating oil-gas suspension system.

[0109] When the vehicle is lightly loaded (including no load), the impact force generated by the vehicle bumping is not sufficient to cause the impact plate 51 to touch neither the pump rod of the first oil source mechanism 2 nor the pump rod of the second oil source mechanism 4, and neither the first oil source mechanism 2 nor the second oil source mechanism 4 obtains a trigger signal; at this time, the low-pressure gas chamber of the double-chamber accumulator 6 is used to achieve the effect of energy absorption and shock absorption, and the pressure oil transmitted from the suspension cylinder 5 to the oil chamber of the double-chamber accumulator 6 is not sufficient to cause the low-pressure gas chamber of the double-chamber accumulator 6 to exceed the limit compression position.

[0110] When the vehicle is overloaded, the piston rod of the suspension cylinder 5 is compressed and moves a certain distance into the suspension cylinder 5. When the vehicle passes through a bumpy road surface, the impact force generated by the vehicle's bumping causes the piston rod of the suspension cylinder 5 to drive the impact plate 51 to vibrate up and down repeatedly, causing the impact plate 51 to repeatedly strike the pump rod of the first oil source mechanism 2 and the pump rod of the second oil source mechanism 4. The pump rods of the first oil source mechanism 2 and the second oil source mechanism 4 perform reciprocating telescopic actions. In addition, when the piston rod of the suspension cylinder 5 retracts, it will press the hydraulic oil in the oil chamber of the suspension cylinder 5 into the oil chamber of the double-chamber accumulator 6.

[0111] When the pump rod of the first oil source mechanism 2 retracts under the action of the impact force provided by the impact plate 51, the oil chamber of the first oil source mechanism 2 transports hydraulic oil to the oil chamber of the air charging device 1 through the output oil port. When the pump rod of the first oil source mechanism 2 extends under the action of the elastic force provided by the second spring 26, the oil chamber of the first oil source mechanism 2 replenishes hydraulic oil through the oil suction port; the oil chamber of the air charging device 1 pushes the first piston 15 to compress the air chamber of the air charging device 1 under the action of the hydraulic oil provided by the first oil source mechanism 2, and the air pressure in the air chamber of the air charging device 1 increases.

[0112] When the pump rod of the second oil source mechanism 4 retracts under the action of the impact force provided by the impact plate 51, the oil chamber of the second oil source mechanism 4 transports hydraulic oil to the input end of the valve assembly 3 through the output oil port. When the pump rod of the second oil source mechanism 4 extends under the action of the elastic force provided by the spring, the oil chamber of the second oil source mechanism 4 replenishes hydraulic oil through the oil suction port.

[0113] When the low-pressure piston 64 in the low-pressure gas chamber of the double-chamber accumulator 6 squeezes the volume of the low-pressure gas chamber of the double-chamber accumulator 6 into the minimum state, the low-pressure piston 64 presses the spool of the third reversing valve 33, causing the third reversing valve 33 to be in the first working position. The oil inlet of the third reversing valve 33 is communicated with the working oil port of the third reversing valve 33. Part of the hydraulic oil input into the valve assembly 3 from the second oil source mechanism 4 acts on the second control end of the first reversing valve 31 through the oil inlet of the third reversing valve 33 and the working oil port of the third reversing valve 33, switching the first reversing valve 31 to the third working position, that is, the oil inlet of the first reversing valve 31 is communicated with the first working oil port of the first reversing valve 31. Part of the hydraulic oil input into the valve assembly 3 from the second oil source mechanism 4 acts on the control end of the third control valve 13 through the oil inlet of the first reversing valve 31 and the first working oil port of the first reversing valve 31, causing the third control valve 13 to conduct reversely. The high-pressure gas compressed in the gas chamber of the air supplement device 1 flows through the second control valve 12 and the third control valve 13 to the low-pressure gas chamber of the double-chamber accumulator 6, realizing the pressurization of the low-pressure gas chamber of the double-chamber accumulator 6. With the pressurization of the low-pressure gas chamber of the double-chamber accumulator 6, the impact of the low-pressure piston 64 on the end cover of the low-pressure cylinder barrel 61 is avoided, and the service life of the double-chamber accumulator 6 is improved. At the same time, because the high-pressure gas chamber of the double-chamber accumulator 6 will work only when the pressure of the low-pressure gas chamber of the double-chamber accumulator 6 is the same as that of the high-pressure gas chamber of the double-chamber accumulator 6, pressurizing the low-pressure gas chamber of the double-chamber accumulator 6 also provides enough compressible space for the high-pressure gas chamber of the double-chamber accumulator 6.

[0114] When the vehicle is unloaded, the low-pressure piston 64 of the low-pressure air chamber of the double-chamber accumulator 6 resets, and the volume of the low-pressure air chamber of the double-chamber accumulator 6 is in the maximum state. The low-pressure piston 64 presses the spool of the second reversing valve 32, causing the second reversing valve 32 to be in the first working position. The oil inlet of the second reversing valve 32 is communicated with the working oil port of the second reversing valve 32. Part of the hydraulic oil input into the valve assembly 3 from the second oil source mechanism 4 acts on the first control end of the first reversing valve 31 through the oil inlet of the second reversing valve 32 and the working oil port of the second reversing valve 32, switching the first reversing valve 31 to the first working position, that is, the oil inlet of the first reversing valve 31 is communicated with the second working oil port of the first reversing valve 31. Part of the hydraulic oil input into the valve assembly 3 from the second oil source mechanism 4 acts on the control ends of the first control valve 11 and the second control valve 12 through the oil inlet of the first reversing valve 31 and the second working oil port of the first reversing valve 31, causing both the first control valve 11 and the second control valve 12 to conduct in the reverse direction. At this time, the first control valve 11 opens the oil discharge channel of the oil chamber of the air replenishing device 1 via the oil discharge port, and the first piston 15 of the air replenishing device 1 acts to compress the oil chamber of the air replenishing device 1, increasing the air chamber of the air replenishing device 1 and reducing the gas pressure in the air chamber of the air replenishing device 1. In addition, the second control valve 12 enables the air vent of the air chamber of the air replenishing device 1 to be used only for unidirectional gas input, and the high-pressure gas in the low-pressure air chamber of the double-chamber accumulator 6 flows back to the air chamber of the air replenishing device 1.

[0115] The above description is only a preferred embodiment of the present invention, and does not impose any form of limitation on the present invention. Any simple modification, equivalent change and modification made to the above embodiments based on the technical essence of the present invention are all within the scope of the technical solution of the present invention.

Claims

1. An air charging and discharging system, characterized in that, Comprising: An air supplement device (1), the air supplement device (1) includes an oil chamber and an air chamber. A first control valve (11) is provided at the oil discharge port of the oil chamber of the air supplement device (1), and a second control valve (12) and a third control valve (13) connected in series are provided at the air vent of the air chamber of the air supplement device (1); A first oil source mechanism (2), the oil output end of the first oil source mechanism (2) is connected to the oil chamber of the air supplement device (1). When the first oil source mechanism (2) obtains a trigger signal, the first oil source mechanism (2) delivers hydraulic oil to the oil chamber of the air supplement device (1); A valve assembly (3), the first output end of the valve assembly (3) is connected to the third control valve (13), and the second output end of the valve assembly (3) is respectively connected to the first control valve (11) and the second control valve (12); A second oil source mechanism (4), the oil output end of the second oil source mechanism (4) is connected to the input end of the valve assembly (3). When the second oil source mechanism (4) obtains a trigger signal, the second oil source mechanism (4) delivers hydraulic oil to the input end of the valve assembly (3); When the input end of the valve assembly (3) is in communication with the first output end of the valve assembly (3), the hydraulic oil flowing out from the first output end of the valve assembly (3) acts on the third control valve (13), so that the air vent of the air chamber of the air supplement device (1) can only be used for unidirectional gas output; When the input end of the valve assembly (3) is in communication with the second output end of the valve assembly (3), the hydraulic oil flowing out from the second output end of the valve assembly (3) acts on the first control valve (11) and the second control valve (12) respectively, so that the oil discharge channel of the oil chamber of the air supplement device (1) via the oil discharge port is opened, and the air vent of the air chamber of the air supplement device (1) can only be used for unidirectional gas input.

2. The air charging and discharging system according to claim 1, characterized in that, The first control valve (11), the second control valve (12) and the third control valve (13) are all pilot-operated check valves. The oil outlet of the first control valve (11) is connected to the oil chamber of the air supplement device (1). The air inlet of the second control valve (12) is connected to the air chamber of the air supplement device (1). The air outlet of the third control valve (13) is connected to the air outlet of the second control valve (12).

3. The air charging and discharging system according to claim 1, wherein The valve assembly (3) includes a first reversing valve (31). The oil inlet of the first reversing valve (31) is connected to the oil output end of the second oil source mechanism (4). The first working oil port of the first reversing valve (31) is connected to the third control valve (13). The second working oil port of the first reversing valve (31) is respectively connected to the first control valve (11) and the second control valve (12); The first reversing valve (31) includes a first working position, a second working position and a third working position; When the first reversing valve (31) is in the first working position, the oil inlet of the first reversing valve (31) is in communication with the second working oil port of the first reversing valve (31); When the first reversing valve (31) is in the second working position, the oil inlet of the first reversing valve (31), the first working oil port of the first reversing valve (31) and the second working oil port of the first reversing valve (31) are all in a cut-off state; When the first reversing valve (31) is in the third working position, the oil inlet of the first reversing valve (31) is in communication with the first working oil port of the first reversing valve (31).

4. The air charging and discharging system according to claim 3, wherein The first reversing valve (31) includes a first control end and a second control end; When a control pressure is input at the first control end, the first reversing valve (31) is controlled to be in the first working position; When a control pressure is input at the second control end, the first reversing valve (31) is controlled to be in the third working position; When there is no control pressure input at both the first control end and the second control end, the first reversing valve (31) is in the second working position.

5. The air charging and discharging system according to claim 1, wherein Both the first oil source mechanism (2) and the second oil source mechanism (4) adopt mechanical oil pumps. The rodless chamber of the mechanical oil pump is the oil chamber. The mechanical oil pump is provided with an oil suction port and an oil output port. The oil suction port and the oil output port of the mechanical oil pump are both communicated with the oil chamber of the mechanical oil pump, and both the oil suction port and the oil output port of the mechanical oil pump are unidirectionally conductive; an elastic element is arranged in the oil chamber of the mechanical oil pump. One end of the elastic element abuts against the piston of the mechanical oil pump, and the other end of the elastic element abuts against the inner side wall of the cylinder bottom of the mechanical oil pump.

6. An oil-gas suspension system capable of automatically adjusting pressure, characterized in that It includes a suspension cylinder (5), a double-chamber accumulator (6), an accumulator (7) installed on the vehicle, and the air charging and discharging system as described in claim 1; The double-chamber accumulator (6) includes a high-pressure gas chamber, a low-pressure gas chamber, and an oil chamber. The oil chamber of the double-chamber accumulator (6) is located between the high-pressure gas chamber and the low-pressure gas chamber. The oil chamber of the double-chamber accumulator (6) is separated from the high-pressure gas chamber and the low-pressure gas chamber by pistons respectively; The rodless chamber of the suspension cylinder (5) is the oil chamber, and the oil chamber of the suspension cylinder (5) is connected to the oil chamber of the double-chamber accumulator (6); The accumulator (7) is arranged on the oil path between the oil output end of the second oil source mechanism (4) and the input end of the valve assembly (3) in the air charging and discharging system; The air charging device (1) in the air charging and discharging system is sequentially connected to the low-pressure gas chamber of the double-chamber accumulator (6) through a second control valve (12) and a third control valve (13); The telescopic movement of the piston rod of the suspension cylinder (5) is used as a signal to trigger the action of the first oil source mechanism (2) and the second oil source mechanism (4) in the air charging and discharging system; When the volume of the low-pressure gas chamber of the double-chamber accumulator (6) is in the minimum state, the valve assembly (3) acts, so that the input end of the valve assembly (3) is communicated with the first output end of the valve assembly (3); When the volume of the low-pressure gas chamber of the double-chamber accumulator (6) is in the maximum state, the valve assembly (3) acts, so that the input end of the valve assembly (3) is communicated with the second output end of the valve assembly (3).

7. The automatically adjustable oil-gas suspension system according to claim 6, characterized in that, The first control valve (11), the second control valve (12), and the third control valve (13) in the air charging and discharging system are all pilot-operated check valves. The oil outlet of the first control valve (11) is connected to the oil chamber of the air charging device (1), the air inlet of the second control valve (12) is connected to the air chamber of the air charging device (1), and the air outlet of the third control valve (13) is connected to the air outlet of the second control valve (12); The valve assembly (3) in the charging and discharging system includes a first reversing valve (31). The oil inlet of the first reversing valve (31) is connected to the oil output end of the second oil source mechanism (4). The first working oil port of the first reversing valve (31) is connected to the control end of the third control valve (13). The second working oil port of the first reversing valve (31) is respectively connected to the control ends of the first control valve (11) and the second control valve (12). The first reversing valve (31) includes a first working position, a second working position and a third working position. When the first reversing valve (31) is in the first working position, the oil inlet of the first reversing valve (31) is communicated with the second working oil port of the first reversing valve (31). When the first reversing valve (31) is in the second working position, the oil inlet, the first working oil port and the second working oil port of the first reversing valve (31) are all in a cut-off state. When the first reversing valve (31) is in the third working position, the oil inlet of the first reversing valve (31) is communicated with the first working oil port of the first reversing valve (31).

8. The automatically adjustable oil-gas suspension system according to claim 7, characterized in that, The first reversing valve (31) includes a first control end and a second control end. When there is a control pressure input at the first control end, control the first reversing valve (31) to be in the first working position. When there is a control pressure input at the second control end, control the first reversing valve (31) to be in the third working position. When there is no control pressure input at both the first control end and the second control end, the first reversing valve (31) is in the second working position. The valve assembly (3) further includes a second reversing valve (32) and a third reversing valve (33). The oil inlet of the second reversing valve (32) is connected to the oil output end of the second oil source mechanism (4). The working oil port of the second reversing valve (32) is connected to the first control end of the first reversing valve (31). The oil return port of the second reversing valve (32) is connected to the oil tank. The second reversing valve (32) includes a first working position and a second working position. When the second reversing valve (32) is in the first working position, the working oil port of the second reversing valve (32) is connected to the oil inlet of the second reversing valve (32). When the second reversing valve (32) is in the second working position, the working oil port of the second reversing valve (32) is connected to the oil return port of the second reversing valve (32). The oil inlet of the third reversing valve (33) is connected to the oil output end of the second oil source mechanism (4). The working oil port of the third reversing valve (33) is connected to the second control end of the first reversing valve (31). The oil return port of the third reversing valve (33) is connected to the oil tank. The third reversing valve (33) includes a first working position and a second working position. When the third reversing valve (33) is in the first working position, the working oil port of the third reversing valve (33) is connected to the oil inlet of the third reversing valve (33). When the third reversing valve (33) is in the second working position, the working oil port of the third reversing valve (33) is connected to the oil return port of the third reversing valve (33).

9. The automatically adjustable oil-gas suspension system according to claim 8, wherein, The second reversing valve (32) includes a first control end and a second control end. The first control end of the second reversing valve (32) is provided with a valve core, the valve core is placed in the hydraulic cavity of the double-chamber accumulator (6), and the valve core at the first control end of the second reversing valve (32) is controlled by the piston in the low-pressure gas cavity of the double-chamber accumulator (6). The first control end of the second reversing valve (32) is used to control the second reversing valve (32) to be in the first working position; A spring is provided at the second control end of the second reversing valve (32) for controlling the second reversing valve (32) to be in the second working position; The third reversing valve (33) includes a first control end and a second control end; The first control end of the third reversing valve (33) is provided with a valve core, the valve core is placed in the low-pressure gas cavity of the double-chamber accumulator (6), and the valve core at the first control end of the third reversing valve (33) is controlled by the piston in the low-pressure gas cavity of the double-chamber accumulator (6). The first control end of the third reversing valve (33) is used to control the third reversing valve (33) to be in the first working position; A spring is provided at the second control end of the third reversing valve (33) for controlling the third reversing valve (33) to be in the second working position.

10. The automatically adjustable oil-gas suspension system according to claim 8, characterized in that, A damping hole is provided on the oil path where the working oil port of the second reversing valve (32) is connected to the first control end of the first reversing valve (31); a damping hole is provided on the oil path where the working oil port of the third reversing valve (33) is connected to the second control end of the first reversing valve (31).

11. The automatically adjustable oil-gas suspension system according to claim 6, wherein, Both the first oil source mechanism (2) and the second oil source mechanism (4) adopt mechanical oil pumps. The rodless cavity of the mechanical oil pump is the oil cavity. The mechanical oil pump is provided with an oil suction port and an oil output port, and both the oil suction port and the oil output port of the mechanical oil pump are communicated with the oil cavity of the mechanical oil pump, and both the oil suction port and the oil output port of the mechanical oil pump are unidirectionally conductive; an elastic element is provided in the oil cavity of the mechanical oil pump, one end of the elastic element abuts against the piston of the mechanical oil pump, and the other end of the elastic element abuts against the inner side wall of the bottom of the cylinder of the mechanical oil pump; Both the first oil source mechanism (2) and the second oil source mechanism (4) are arranged on the cylinder block of the suspension cylinder (5), and the first oil source mechanism (2) and the second oil source mechanism (4) are respectively located on both sides of the suspension cylinder (5). An impact plate is provided on the piston rod of the suspension cylinder (5). The pump rods of the first oil source mechanism (2) and the second oil source mechanism (4) are both on the movement track of the impact plate, and the distance between the pump rod of the first oil source mechanism (2) and the impact plate is equal to the distance between the pump rod of the second oil source mechanism (4) and the impact plate.

12. A voltage regulation method, characterized in that, Including the automatically adjustable oil-gas suspension system as described in claim 11; When the vehicle is lightly loaded, the impact plate does not touch the pump rod of the first oil source mechanism (2) and the pump rod of the second oil source mechanism (4), and neither the first oil source mechanism (2) nor the second oil source mechanism (4) obtains a trigger signal; When the vehicle is heavily loaded, the piston rod of the suspension cylinder (5) is compressed and moves a certain distance into the suspension cylinder (5). When the vehicle passes through a bumpy road surface, the piston rod of the suspension cylinder (5) drives the impact plate to vibrate up and down repeatedly, causing the impact plate to repeatedly strike the pump rods of the first oil source mechanism (2) and the second oil source mechanism (4). The pump rods of the first oil source mechanism (2) and the second oil source mechanism (4) perform reciprocating telescopic actions. In addition, when the piston rod of the suspension cylinder (5) retracts, the hydraulic oil in the oil chamber of the suspension cylinder (5) is pressed into the oil chamber of the double-chamber accumulator (6). When the pump rod of the first oil source mechanism (2) retracts under the action of the impact force provided by the impact plate, the oil chamber of the first oil source mechanism (2) delivers hydraulic oil to the oil chamber of the air charging device (1) through the oil outlet. When the pump rod of the first oil source mechanism (2) extends under the action of the elastic force provided by the elastic element, the oil chamber of the first oil source mechanism (2) replenishes hydraulic oil through the oil suction port; the piston in the oil chamber of the air charging device (1) is pushed by the hydraulic oil provided by the first oil source mechanism (2) to compress the air chamber of the air charging device (1). When the pump rod of the second oil source mechanism (4) retracts under the action of the impact force provided by the impact plate, the oil chamber of the second oil source mechanism (4) delivers hydraulic oil to the input end of the valve assembly (3) through the oil outlet. When the pump rod of the second oil source mechanism (4) extends under the action of the elastic force provided by the elastic element, the oil chamber of the second oil source mechanism (4) replenishes hydraulic oil through the oil suction port; When the piston in the low-pressure gas chamber of the double-chamber accumulator (6) squeezes the volume of the low-pressure gas chamber of the double-chamber accumulator (6) to the smallest state, the input end of the valve assembly (3) is in communication with the first output end of the valve assembly (3). The hydraulic oil flowing out from the first output end of the valve assembly (3) acts on the third control valve (13), so that the air vent of the air chamber of the air charging device (1) can only be used for one-way gas output. The compressed high-pressure gas in the air chamber of the air charging device (1) flows into the low-pressure gas chamber of the double-chamber accumulator (6) to realize the pressurization of the low-pressure gas chamber of the double-chamber accumulator (6). When the vehicle is unloaded, the piston in the low-pressure gas chamber of the double-chamber accumulator (6) resets, and the volume of the low-pressure gas chamber of the double-chamber accumulator (6) is in the maximum state. The input end of the valve assembly (3) is in communication with the second output end of the valve assembly (3). The hydraulic oil flowing out from the second output end of the valve assembly (3) acts on the first control valve (11) and the second control valve (12) respectively. At this time, the first control valve (11) opens the oil discharge channel of the oil chamber of the air charging device (1) via the oil discharge port, and the piston of the air charging device (1) moves, causing the air chamber of the air charging device (1) to increase, and the gas pressure in the air chamber of the air charging device (1) to decrease. In addition, the second control valve (12) makes the air vent of the air chamber of the air charging device (1) can only be used for one-way gas input, and the high-pressure gas in the low-pressure gas chamber of the double-chamber accumulator (6) flows back to the air chamber of the air charging device (1).

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