Pressure regulating overflow device

Abstract

The pressure regulating overflow device comprises a main gas circuit formed by an overflow valve and a slave gas circuit formed by two electromagnetic valves, the main gas circuit and the slave gas circuit take total air supply as input, and the slave gas circuit can supplement air pressure into a pressure building cavity of the overflow valve, so that the output pressure of the overflow valve is changed under the condition that the fixed overflow pressure of the overflow valve is not adjusted. The technical problem that the manual control adjustment efficiency of the pressure regulation overflow end is poor in the high-frequency change scene of the pressure supply requirement is solved.

Description

Technical Field

[0001] The invention relates to the technical field of fluid control for special vehicles, and in particular to a pressure regulating overflow device for adjusting the air pressure in an air spring on a rail vehicle. Background Art

[0002] The overflow valve is a fluid release device that sets a critical conduction pressure to limit fluid output, so that the pipeline or system can output dynamically and constantly at the desired pressure. It is usually configured to include two working states: overflow cutoff and overflow release. Overflow cutoff means that if the fluid input pressure does not reach the critical pressure (set conduction pressure), the output end of the valve body will be in a closed cutoff state, and once the fluid input pressure exceeds the "set conduction pressure", the valve port will release the overflow cutoff state and be conducted, and then the fluid will be output to the downstream equipment in an overflow release state.

[0003] An overflow valve structure in the prior art is taken as an example. Figure 1 In the cross-sectional structure of the known overflow valve shown, the overflow valve 100' includes a piston chamber 102' with an elastic component 101' to build pressure, and an input port 103' and an output port 104', each of which is connected to the piston chamber 102' through a pipeline. The two ends of the elastic component 101' are respectively defined as a pressure-bearing end that is subjected to force to build pressure, and a fixed end that is fixed to the valve core 105' to apply pressure. The force on the pressure-bearing end comes from the tightening force of the top of the elastic component 101' along the pressure-building direction. The tightening force makes the elastic component 101' always maintain the tendency of overcoming its own deformation, so as to apply an action pressure to the valve core through its fixed end in the pressure-building direction. The action pressure presses the valve core 105' and the valve port to form a closed state. The closed state is also the overflow cut-off state of the overflow valve, and the pressure borne by the valve core 105' in this state is also the aforementioned "set conduction pressure", or overflow pressure.

[0004] Continue to view Figure 1 In the existing structure shown, only when the fluid pressure at the input port is greater than or equal to the aforementioned overflow pressure, the valve core 105' will be pushed away from the valve port, and then the conduction between the output port and the valve port will be established. In the known overflow valve scheme, the specific setting of the overflow pressure is mostly achieved by changing the tight fit between the adjusting screw and the pressure block at the pressure-bearing end of the elastic component 101', that is, the deformation of the elastic component 101' is changed by loose or tight fitting of the adjusting screw, so as to adjust the size of the overflow pressure.

[0005] However, this manual adjustment method is difficult to apply in scenarios where the fluid input and output pressure requirements show high-frequency changes. For example, most rail transit vehicles today use a complete vehicle air control assembly. Since the air control requirements of the equipment at each air-using node are different, the input and output air pressures of most node equipment are adjusted individually after the total air supply. In this way, at some nodes where control intervention is more frequent, the overflow pressure is repeatedly adjusted by manually adjusting the screw, which results in poor control efficiency and accuracy. Summary of the invention

[0006] In view of this, the present invention provides a pressure regulating overflow device to solve at least one of the above problems.

[0007] In order to solve the above technical problems, in the pressure-regulating overflow device provided in the preferred embodiment of the present invention, a gas path is led out from the total air supply end, and the gas path is connected to the pressure-building chamber of the overflow valve. When the gas path is opened, the gas pressure in the pressure-building chamber is superimposed on the fixed overflow pressure of the overflow valve, so that the gas supply demand at the gas supply end is increased, and a larger input pressure is required to push the valve core away from the valve port. Corresponding to the gas supply pressure after the boost, the overflow output pressure of the overflow valve is also increased.

[0008] On this basis, as a preferred solution of the preferred embodiment of the present invention, the slave gas circuit is specifically configured, and the slave gas circuit is divided into a first branch and a second branch by two electrically controlled valves that realize the gating function. The control unit makes a gating between the first branch and / or the second branch, so that the slave gas circuit switches between the three working conditions of gas supply, pressure relief and pressure stabilization. Thus, while avoiding the pressure loss caused by the gas supply end always supplying gas, an additional pressure reduction means after the overflow pressure is increased is added. In addition, under this control strategy, an additional pressure regulating valve located at the air inlet end of the first branch can be added. The pressure regulating valve is used as a temporary pressure fine-tuning means of the slave gas circuit here. According to the road conditions, ambient temperature and other conditions, the input pressure of the slave gas circuit can be intervened to avoid overcurrent and overpressure. When the first or second solenoid valve fails, the pressure regulating valve can also be used as a temporary switch mode to close the gas supply of the slave gas circuit to ensure the safe operation of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] Figure 1 is a cross-sectional view showing a cross-sectional structure of a known overflow valve;

[0010] Figure 2 is a schematic diagram showing the framework structure of a pressure regulating overflow device in a preferred embodiment of the present invention;

[0011] Figure 3 is a cross-sectional view showing the cross-sectional structure of the overflow valve in the preferred embodiment of the present invention;

[0012] Figure 4is a cross-sectional view showing the cross-sectional structure of the first solenoid valve in the preferred embodiment of the present invention;

[0013] Figure 5 is a cross-sectional view showing Figure 4 A side sectional structure of the first solenoid valve shown;

[0014] Figure 6 is a cross-sectional view showing the cross-sectional structure of the second solenoid valve in the preferred embodiment of the present invention;

[0015] Figure 7 is a cross-sectional view showing Figure 6 The side cross-sectional structure of the second solenoid valve is shown. DETAILED DESCRIPTION

[0016] Replay Figure 1 The existing scheme shown, the known technical understanding is that the overflow pressure can only be adjusted by rotating the adjusting screw, and the output pressure value of the overflow valve can be changed accordingly. In actual use, in order to avoid frequent rotation adjustment, the known scheme can try to improve the inconvenience of adjusting the overflow pressure at the input end and / or output end of the overflow valve by introducing an additional air source and using supplementary pressure as a means. An easily conceivable solution is, for example, to respectively set an air intake branch connected to the main air source or the additional air source at the input end and the output end, so that the input air pressure or the supplementary output air pressure can be adjusted by the fluid pressure of the supplementary air source, while the overflow pressure of the overflow valve itself remains unchanged. However, it is obvious that, on the one hand, the pipelines added in this way will make the overall system flow channel configuration redundant, and on the other hand, it is difficult to ignore the increased control end processing load due to the additional control logic.

[0017] For example, the bottom of each carriage of the EMU will be equipped with an empty spring module. The empty spring module is a pressure device that compresses gas and changes the gas pressure to make the gas provide elasticity. The bottom of the carriage is equipped with such an empty spring module in the hope that the elastic support force provided by the module can be dynamically adjusted according to the different loads and driving speeds of the train by inflating and exhausting the module, so that the carriage can always be in a relatively stable position and state during the driving of the EMU. In this way, the acceleration and braking of the vehicle during driving, as well as the passenger experience when the vehicle is driving in a scene with high undulations in the track, will be effectively improved. The execution of the empty spring module depends on a pressure regulating system that is configured at the front end to adapt to the pressure changes of the module. In the existing architecture of the pressure regulating system, the pressure regulating output capability of the relief valve is mostly used to achieve pressure control and constant pressure of the air spring module. However, in some scenarios with complex and changing road conditions or severe ambient temperature conditions, the car air spring module is required to have a higher adjustment frequency, which will correspondingly require the relief pressure of the relief valve in its front-stage pressure regulating system to be able to respond quickly to changes in operating conditions. Within this demand range, the problems of poor control efficiency and accuracy of manually adjusting the relief pressure will be further amplified.

[0018] On the other hand, referring to the known solutions of introducing additional air source pipelines, the problem encountered is that since the air pressure input of the overflow valve connected to the front stage of the air spring module is mostly supplied by the total wind pressure, and due to the limitation of the vehicle pressure control, the total wind pressure is often not a controllable and definite value, but the priority is the air supply of multiple nodes of the vehicle. This makes the air supply pressure of the equipment at the specific node position in the local area of ​​the system only able to follow the change of the total wind pressure and present an uncontrollable state. Therefore, the attempt to adjust the input air supply pressure to control the overflow valve's final output to the air pressure of the air spring module is not feasible. And for the same reason, the method of adding air replenishment equipment to the pipeline from the overflow valve to the air spring module also has many limitations and shortcomings.

[0019] In view of the above technical problems and limitations, the preferred embodiments of the present invention solve the problems mainly in two aspects:

[0020] First, since manual adjustment is not desired, in other words, it is not desired to adjust the pressure of the elastic component on the valve core by rotating the adjusting member, it is possible to try to change the pressure of the piston chamber (pressure-building chamber) to supplement the elastic force generated by the elastic component; for example, a controllable pressure-regulating branch is led out from the input end, and the pressure-regulating branch is configured to replenish gas into the pressure-building chamber when the overflow pressure increases, as "supplementary overflow pressure";

[0021] Secondly, the adjustment of the overflow pressure is not always a pressurization requirement, but should at least include the pressure reduction situation after the overflow pressure is increased by the aforementioned pressure regulating branch. Under different pressure regulation requirements, the maintenance and release of the pipeline pressure should also be considered when configuring the aforementioned controllable pressure regulating branch, that is, the pressure building and pressurization effects of the overflow valve pressure building chamber can be adaptively adjusted as the overflow demand changes.

[0022] The following will focus on the above-mentioned improvement ideas and refer to the accompanying drawings to describe the embodiments of the present invention. It will be appreciated by those skilled in the art that the described embodiments can be modified in various ways without departing from the spirit and scope of the present invention. Therefore, the drawings and descriptions are illustrative in nature and are not intended to limit the scope of protection of the claims. In addition, in this specification, the drawings are not drawn to scale and the same reference numerals represent the same parts.

[0023] It should be noted that the expressions “first” and “second” used in the embodiments of the present invention are intended to distinguish two non-identical entities with the same name or non-identical parameters. It can be seen that “first” and “second” are only for the convenience of expression and should not be understood as limitations on the embodiments of the invention. The subsequent embodiments will not explain this one by one.

[0024] Figure 2 The schematic diagram shows the framework structure of the pressure regulating overflow device in a preferred embodiment of the present invention. Figure 2 The illustrated method divides the illustrated structure into a main gas path 10 (located at the bottom of the main gas path) with the total wind pressure 100 as the input, and the overflow valve 200 as the output to the lower level gas consumption. Figure 2 Below), and from the total wind pressure 100 air supply as input, the pipeline extends to the overflow valve pressure chamber 201 chamber from the gas line 20 (located Figure 2 In the preferred embodiment of the present invention, the relief pressure of the relief valve 200 is set to a fixed value, that is, it is not expected to adjust the relief pressure by adjusting the screw during the vehicle travel. Therefore, an attempt is made to supplement the air pressure from the air circuit 20 to the pressure-building chamber of the relief valve, thereby increasing the pressure of the pressure-building chamber 201 to change the relief valve output without changing the relief pressure setting of the relief valve itself.

[0025] First look at the main gas path. Figure 3 is a cross-sectional view showing a cross-sectional structure of a relief valve in a preferred embodiment of the present invention. Figure 1 Compare Figure 3In addition to being set to not change the overflow pressure by adjusting the screw rod, the overflow valve 200 in this embodiment also has a difference from the existing structure, mainly in that a gas replenishment hole 203 corresponding to the slave gas path 20 is opened on the cavity wall of the pressure building cavity 201. The gas replenishment hole 203 is a hole-shaped structure that leads from the outer cavity wall of the pressure building cavity 201 to its inner cavity, and the slave gas path 20, that is, through the gas replenishment hole 203, replenishes gas to the inner cavity of the pressure building cavity 201. In terms of pressure, the elastic component 204 in the pressure-building chamber of the relief valve 200 is forced to maintain a fixed deformation, and this deformation generates a fixed pressure that abuts the valve core 205 against the valve port. Therefore, when the slave gas circuit 20 is closed, the relief valve 200 on the main gas circuit 10 should also output an overflow at a fixed pressure value. When the slave gas circuit 20 replenishes air to the inner cavity of the pressure-building chamber 201 through the air replenishing hole 203, the abutment force between the valve core 205 and the valve port 206 is enhanced due to the increase in gas pressure in the pressure-building chamber 201, resulting in a greater pressure at the input end of the relief valve 200 to push the valve core 205 away from the valve port 206 to achieve overflow output.

[0026] It should be pointed out that when the overflow pressure increases to the point where the valve core 205 is pushed away from the valve port 206 to generate overflow output, the pressure at the input end 207 will drop instantaneously during the period of time due to the pressure loss caused by the work at the moment when the valve core 205 is pushed open, which will force the valve core 205 and the valve port to turn to a closing trend due to the pressure loss at the input end. Then, this closing trend of the valve core and the valve port will cause the pressure at the input end to increase due to the channel constriction, and then the valve core 205 and the valve port will turn to an opening trend again. In this way, when a certain continuous pressure input is maintained at the input end, the valve core of the overflow valve will always maintain this dynamic equilibrium state that repeats between the opening and closing trends, and correspondingly, the overflow output value of the overflow valve will also fluctuate within the value range determined by the fixed pressure value during the aforementioned time period and converge to the fixed value.

[0027] Let's talk about the secondary gas circuit 20. Regarding the configuration of the secondary gas circuit 20, the preferred embodiment of the present invention focuses on realizing that:

[0028] 1) To meet the needs of pressure control and adjustment, the slave gas circuit should include at least one on-off mechanism to control the on-off of the gas circuit. When the overflow pressure output is fixed by the overflow valve, the slave gas circuit is closed; and when the overflow output of the overflow valve needs to be increased, the slave gas circuit is opened;

[0029] 2) The air circuit is input with the total wind pressure of continuous air supply. Once the air circuit intervenes in pressure control, the pressure inside it will continue to maintain the pressure at the air supply end, which will make the increased overflow pressure unable to return to the initial value. Therefore, necessary release means are required so that the increased overflow pressure can be released to the initial pressure value of the corresponding overflow valve fixed overflow pressure.

[0030] The preferred embodiment of the present invention also noted that after the disconnection mechanism and the release mechanism are introduced respectively, another problem will be encountered. When the disconnection mechanism intervenes to make the slave gas path conduct, the release mechanism should not be intervened, otherwise the supplementary gas will be released out of the system; similarly, when the release mechanism intervenes to release the overflow pressure increased by the overflow valve, if the disconnection mechanism intervenes, it will lead to the loss of the total wind pressure. Even if the disconnection mechanism and the release mechanism are configured to intervene (conduct) in a selective manner, there will still be a problem that the pressurization effect of the slave gas path on the pressure chamber of the overflow valve cannot be maintained.

[0031] In view of the above aspects and problems, in a preferred embodiment of the present invention, the slave gas circuit is configured to sequentially configure the first switch and the second switch in the gas supply direction from the total air supply to the gas supply hole. The first switch is used as the main switch of the slave gas circuit. When the overflow pressure of the overflow valve needs to be increased, the first and second switches are opened respectively. Here, for the convenience of explanation, this moment is temporarily set as the first moment. Thereafter, in order to maintain the pressure created in the first moment, the first switch is first closed so that the gas supply end is no longer input, and the second switch is kept open at the same time, so that the supplementary gas filled in the first moment maintains the pressure in the pipeline from the second switch to the pressure-building chamber, and this moment is set as the second moment. Finally, when the overflow output pressure demand decreases, the first switch remains closed while the second switch is opened. In this way, the pressure maintained in the pressure-building chamber from the second switch is released through the second switch, and the overflow valve pressure is restored to the initial fixed overflow pressure value. After satisfying the pressure control and release, in a specific scenario, it is also necessary to configure control for the first switch and the second switch so that the first and second switches can be manually opened and closed. For example, in a rail vehicle, the first switch and the second switch can be connected to the vehicle electronic control unit (such as ECU), and the control unit is configured to control the on and off of the first switch and the second switch according to the pressure sensing device at the output end of the overflow valve.

[0032] The specific configuration of the first switch and the second switch can be selected from a variety of valves commonly used in pipelines, such as pneumatic valves, hydraulic valves, solenoid valves, etc. Considering the configuration of the vehicle master control unit and the sensitivity requirements of the valve body, in some preferred embodiments of the present invention, two solenoid valves are configured to serve as the first switch and the second switch respectively. According to the technical guidance of the present invention, those skilled in the art can combine the present invention with the knowledge of the present invention. Figure 2 , other valves or known shut-off mechanisms can be selected to achieve the gating function of the first switch and the second switch.

[0033] See also Figure 4 , Figure 4The first solenoid valve in the preferred embodiment is shown, which is referred to as the first solenoid valve for convenience of explanation. The valve body of the first solenoid valve 300 can be roughly divided into two parts. One is the electromagnetic drive unit that realizes the solenoid valve to attract and generate driving force, and the other is the air flow channel from the air inlet 301 of the solenoid valve 300 to the exhaust port 302, and the piston assembly in the air flow channel that controls the corridor selection state. The electromagnetic head 3031 in the electromagnetic drive unit 303 is an energized conductor. When it is energized, it generates magnetic attraction to attract the valve core (moving iron core) 3032 to produce displacement, and maintains the displacement stroke when it is energized until it is released after the energization state ends. At the same time, it also includes an elastic member 3033 (spring) that cooperates with the valve core 3032. The elastic member is configured so that one end is fixed to the body of the solenoid valve 300 and the other end extends into the valve core. When power is not supplied, the tension of the relaxed elastic member 3033 will push the valve core 3032 to the preset position, which is a position where it abuts against the piston assembly to form a tight seal. When power is supplied, the electromagnetic head 3031 conducts electricity to attract the valve core 3032, and the displacement stroke maintained by the valve core 3032 will compress the elastic member 3033 so that it has a certain tension to restore the elastic deformation. This tension will serve as a restoring force for the valve core 3032 to return to the preset position after the electromagnetic head 3031 is powered off.

[0034] The transmission result of the displacement of the valve core 3032 can be seen in Figure 5 As shown in the side cross-sectional view, the valve core 3032 in the valve body is fixedly connected to a connecting rod 3034 at the extended end toward the piston assembly, and the connecting rod is connected to the piston assembly. In other words, the stroke generated by the valve core 3032 will drive the connected part of the piston assembly to produce a movement trend in the same direction. Figure 4, a communication air flow passage is formed between the air inlet 301 and the air outlet 302 within the valve body, and the piston assembly is disposed within this flow passage. The piston assembly includes a frustum-shaped fixed seal 3035 disposed near the air flow passage on the side where the air inlet 301 is located, and a first movable member 3036 disposed near the air flow passage on the side where the air outlet 302 is located and docked with the aforementioned link member 3034. The fixed seal 3035 and the first movable member 3036 are combined to form a kinematic pair that can reciprocate within the air flow passage. The first movable member 3036 is preferably made of a soft sealing material, such as a block made of common rubber or vulcanized material. In the non-energized state, driven by the link member 3034, the first movable member 3036 will be pressed against the fixed seal 3035 to establish a tight seal therebetween. At this time, the gas at the air inlet 301 cannot pass through the air flow passage and be discharged from the air outlet 302, that is, the solenoid valve is cut off. After the solenoid head 3031 is energized, it has a magnetic suction force and attracts the metal valve core 3032 thereto. The movement of the valve core 3032 towards the solenoid head 3031 will be transmitted to the first movable member 3036 by the link member 3034, driving the first movable member 3036 to displace away from the fixed seal 3035. The tight seal between the first movable member 3036 and the fixed seal 3035 is thus released. At this time, the gas at the air inlet 301 can pass through the opened valve port and be discharged from the air outlet 302 through the air flow passage.

[0035] It should be understood that the structure of the first solenoid valve 300 described above is only a schematic explanation for illustrative purposes. In different preferred embodiments of the present invention, the structure of the first solenoid valve 300 can be selected from existing pneumatic control solenoid valves according to control requirements, or can be an improvement based on the structure disclosed in this preferred embodiment. Continuing to refer to Figure 4 , for example, in this preferred embodiment, the air flow passage from the air inlet 301 to the air outlet 302 is set in a "C" shape, which can also be regarded as setting the air inlet 301 and the air outlet 302 to be approximately on the same side of the valve body. In different preferred embodiments, the air inlet 301 and the air outlet 302 can also be set on opposite sides of the valve body. Correspondingly, the extended pipeline of the air flow passage will have a "zigzag" structure. Of course, for this reason, in different embodiments, it is also necessary to correspondingly modify the structure of the piston assembly, or adjust the preset state of the elastic member to change the preset position of the first movable member 3036, and adjust the height difference between the axis of the air inlet 301 pipe orifice and the axis of the air outlet 302 pipe orifice in the vertical direction to adapt to the selection mode of piston assemblies with different structures. For the above possible improvements, they will not be listed and described here, but the preferred embodiments of the present invention should not be limited by the specific structure and configuration of the aforementioned solenoid valve.

[0036] Next, look at the second solenoid valve. As a control component for implementing the aforementioned second switching function, the configuration idea of the second solenoid valve is:

[0037] First, it should have two different pipelines that are wholly or at least partially independent inside, respectively dealing with the air supplement demand and the exhaust release demand. In the case where the two pipelines are partially independent, that is, the air supplement pipeline and the exhaust pipeline share a part of the passage, usually the intake part of the solenoid valve.

[0038] Second, after the pipelines are separated to be independent or partially independent, an alternative control should also be configured, that is, to selectively connect between the air supplement pipeline and the exhaust pipeline, so that the solenoid valve will not have the situation of simultaneous air supplement and exhaust.

[0039] The second solenoid valve 400 in this preferred embodiment is to realize the function of the aforementioned second switch, which is a feasible improvement attempt based on the structure of the first solenoid valve 300. For details, please refer to Figure 6 and Figure 7 the front view and side view cross-sectional structures shown. The difference between the second solenoid valve 400 and the first solenoid valve 300 is that it includes an input port 401 corresponding to the intake port 301 of the first solenoid valve, and two output ports with different functions, namely the air supply port 402 and the pressure relief port 403. In this way, the air flow path formed inside the second solenoid valve 400 includes one input and two outputs. And, for adapting to the pipeline change, adjustments are made to the structure of the first solenoid valve 300. The adjustment method is that in the connection structure of the first solenoid valve 300, the air supply output state when the first movable part 3036 is disengaged from the fixed seal 3035 is kept unchanged, and in this state, the aforementioned air supplement pipeline is导通; at the same time, when the first movable part 3036 of the first solenoid valve 300 is tightly sealed with the fixed seal 3035, the aforementioned exhaust pipeline is导通.

[0040] For the convenience of distinction and description, the names of the same components of the second solenoid valve 400 and the first solenoid valve 300 are retained, while the names of the different components between the two are distinguished, so as to form the continuation of the same names between the two and avoid unnecessary ambiguity. For example, in the second solenoid valve 400, the name of the same fixed seal 3035 in the first solenoid valve 300 is retained, but the names of the input and output ports with different functions, as well as the different movable parts with different sealing states, are distinguished. Looking back accordingly Figure 4 Compare Figure 6 According to Figure 6 the direction shown, the air supplement pipeline 404 and the exhaust pipeline 405 each form a "匚" shape and share the same intake part. In the driving direction of the connecting rod 3034, the pressure relief port 403 is arranged close to the valve core 205, the air supply port 402 is arranged far from the valve core 205, and in the driving direction, the air supply port 402 is located between the pressure relief port 403 and the input port 401.

[0041] According to different considerations of air supply and pressure relief, compared with the first solenoid valve 300, the position of the second movable member 406 in the second solenoid valve 400 should form two different seals, and the two sealing states are alternative choices. Specifically, looking back Figure 4 In the first solenoid valve 300, the preset position of the first movable member 3036 in the valve body is the position where it abuts against the fixed seal. In the second solenoid valve 400, this position is defined as the first preset position, and then the final position of the displacement stroke of the second movable member 406 driven by energizing and attracting the valve core 3032 by the solenoid head 3031 is set as the second preset position. Then, the improvement of the second solenoid valve 400 is that it is expected that when the second movable member 406 is in the first preset position, it maintains the same air supply state as the first solenoid valve 300, that is, the state where the air supply pipeline 404 is导通, and it is expected that when it is in the second preset position, the air supply pipeline 404 is截止 and the exhaust pipeline 405 is导通. Accordingly, the alternative selection of the air supply pipeline and the exhaust pipeline is realized.

[0042] Looking back Figure 4 , when the solenoid head 3031 conducts electricity to attract the valve core 3032 to displace, the connecting rod member 3034 drives the first movable member 3036 to move towards the direction of the valve core 3032, and finally abuts against the surface of the conical protrusion 407 formed in the inner cavity of the valve body at this position. To achieve the above improvement purpose of the second solenoid valve 400, in the valve body of the second solenoid valve 400, the same conical protrusion 407 is made into a through member, so that it can connect the pipeline near the air supply port 402 and the pipeline near the pressure relief port 403, that is, it can connect the air supply pipeline and the exhaust pipeline, and is selectively connected by the reciprocating movement of the second movable member 406 between the first and second preset positions. In this way, when the second movable member 406 is in the first preset position, the gas in the pipeline corresponding to the air supply port 402 will pass through the gap between the second movable member 406 and the valve body, enter the exhaust pipeline through the through conical protrusion 407, and finally be discharged to the outside of the system.

[0043] Similar to the first solenoid valve 300, those skilled in the art can also reproduce the function of the second switch according to the same idea by using different structures of the second solenoid valve. Similarly, for example, adjust the positions and heights of the input port, air supply port, and pressure relief port so that the extension mode of the internal air flow path is approximately in the shape of "丩", etc. Based on the same original part as the first solenoid valve part, more improvement interfaces of the second solenoid valve are not listed in this preferred embodiment.

[0044] Then, connect the first solenoid valve 300 and the second solenoid valve 400 to the vehicle control unit (C) respectively, and configure a pressure sensor (P) at the output side of the overflow valve 200 to sense the air pressure there. Thus, the basic frame structure of the present invention as Figure 1 shown is formed. The actual working conditions include the following process:

[0045] Under the preset working condition, the control unit controls the first solenoid valve and the second solenoid valve to close. Figure 1 In the system shown, only the main air path 10 participates in the overflow output. When the total air supply input reaches the fixed overflow pressure of the overflow valve, the overflow valve outputs air supply to the downstream equipment. The overflow output pressure at this time is defined as the first output air pressure.

[0046] When the air pressure demand of the lower-level equipment increases, for example, when the vehicle is driving on a bumpy road, the air spring module at the bottom of the car needs a larger supporting air pressure output, and the system faces a boost demand. Under this working condition, the control unit controls the first and second solenoid valves to be powered on at the same time. While the total air supply is in progress, it also enters the inner cavity of the overflow valve pressure-building chamber 201 through the air supply hole 203 from the air path 20. Under the influence of the increase in the inner cavity pressure, a larger air supply pressure is required to satisfy the output end of the overflow valve to output to the lower-level equipment. Here, the overflow output pressure under the boost demand is defined as the second output air pressure. It should be understood that the magnitude of the second output air pressure is greater than the magnitude of the first output air pressure.

[0047] Next, two actual working conditions are set. The first is that the vehicle needs to pass through a continuous bumpy road section; the second is that the vehicle returns to a stable road condition after passing through a bumpy road section. For the former, it can be regarded as that the overflow output of the overflow valve needs to maintain the second output air pressure for a certain period of time, that is, the system faces a pressure stabilization demand. For the latter, it can be regarded as that the overflow output of the overflow valve needs to return to the first output air pressure from the second output air pressure at the previous moment, and the system also faces a pressure relief demand.

[0048] Under the requirement of pressure stabilization, the control unit controls the first solenoid valve to close, and the second solenoid valve to open and be in the gas supply state. At this time, the supplementary gas at the previous moment will remain in the pipeline and cavity from the second solenoid valve to the pressure-building cavity of the overflow valve, and maintain a certain gas pressure. Under the pressure relief condition, the control unit controls the first and second solenoid valves to close, and the second solenoid valve is in the exhaust state. At this time, the gas supply end still does not output from the gas circuit 20, and the aforementioned gas maintained in the pipeline and cavity from the second solenoid valve to the pressure-building cavity of the overflow valve will flow back through the gas supply port of the second solenoid valve 400 and be discharged through its pressure relief port 403.

[0049] The function of the pressure sensor (P) is to collect the output pressure of the overflow valve and send the pressure sensing data to the outside of the control unit. When the overflow output pressure reaches the expected value, it is fed back to the main control unit and the control system switches to the corresponding state. Through the above-mentioned setting, the preferred embodiment of the present invention realizes that the overflow output pressure of the overflow valve is adjusted by air replenishment under the premise of fixing the overflow pressure of the overflow valve, and solves the technical problems of poor pressure control efficiency and control accuracy in the overflow pressure regulation scene with high-frequency changes in the supply pressure demand. Of course, in some other embodiments, it is also possible to consider setting a pressure regulating valve 500 at the front stage position of the first solenoid valve 300. During the vehicle travel or non-travel, the pressure regulating valve 500 is used as a temporary pressure fine-tuning means for the slave gas circuit. According to the road conditions, ambient temperature and other conditions, the input pressure of the slave gas circuit can be intervened to avoid overcurrent and overpressure. When the first or second solenoid valve fails, the pressure regulating valve can also be used as a temporary switch mode to close the gas supply from the gas circuit to ensure the safe operation of the system.

[0050] The above embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present invention. It should be pointed out that, for a person of ordinary skill in the art, several modifications and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the present invention patent shall be subject to the attached claims.

Claims

1. A pressure regulating overflow device, comprising: The overflow valve has a fixed overflow pressure, comprising at least one input end connected to the front-stage gas supply, an output end connected to the rear-stage gas supply, and a pressure-building chamber for maintaining a fixed pressure. A pressure regulating branch, the pressure regulating branch includes a first branch and a second branch in the gas supply direction, and is configured as a pipeline that uses the previous stage gas supply as input through the first branch and outputs to the pressure building chamber through the second branch, the first branch includes at least one controlled conduction solenoid valve, and the second branch includes at least one controlled closed exhaust valve, A master control unit, which controls the opening and closing of the solenoid valve and the exhaust valve; The air pressure sensor senses the output pressure of the overflow valve and sends an air pressure data signal to the master control unit, wherein: Under the pressure regulating condition, the master control unit controls the solenoid valve and / or the exhaust valve according to the air pressure data signal to supply air to the first branch and the second branch, or to exhaust air from the second branch.

2. The pressure regulating overflow device according to claim 1, wherein: Under the supercharging condition, the master control unit controls the solenoid valve to open and the exhaust valve to close according to the air pressure data signal to increase the overflow output pressure of the overflow valve, and, Under the pressure relief condition, the master control unit controls the solenoid valve to close and the exhaust valve to open according to the air pressure data signal to reduce the overflow output pressure of the overflow valve.

3. The pressure regulating overflow device according to claim 2, wherein: The pressure-building chamber wall of the overflow valve includes an air-injection through hole, which is formed on the outer chamber wall of the pressure-building chamber and connected to the inner chamber of the pressure-building chamber. The output end of the second branch is connected to the air-injection through hole.

4. The pressure regulating overflow device according to claim 3, wherein: The solenoid valve is a normally closed valve, so that the pressure regulating branch is in a non-pressure regulating cut-off state under normal conditions, and the solenoid valve is controlled to open so that the front-stage air supply end supplies air to the second branch; The exhaust valve includes an input port connected to the first branch, and at least one air supply port and a pressure relief port. The exhaust valve uses the air supply port to form an air supply pipeline connected from the input port to the air supply through hole in the air supply direction, and uses the pressure relief port to form an exhaust pipeline from the air supply through hole to the outside of the pipeline. The exhaust valve is controlled so that one of the pressure relief port and the air supply port is connected.

5. The pressure regulating overflow device according to any one of claims 2 to 4, wherein: The air supply port is a normally closed port, and the pressure relief port is a normally open port. Under the boosting condition, the air supply port is opened, the pressure relief port is closed, and the front-stage air supply enters the pressure-building chamber through the air supply hole; Under the pressure relief condition, the air supply port is closed, the pressure relief port is opened, the air pressure in the pressure building chamber is discharged from the pressure relief port, and, Under the pressure-maintaining condition, the master control unit controls the solenoid valve to be closed, and controls the air supply port of the exhaust valve to be opened and the pressure relief port to be closed according to the air pressure data signal.

6. The pressure regulating overflow device according to claim 5, wherein: The solenoid valve comprises an air inlet and an exhaust port, and a first air flow passage from the air inlet to the exhaust port is formed inside the solenoid valve, and the valve body also comprises: The electromagnetic drive unit is composed of an electromagnetic head, a valve core and an elastic component. A first fixed seal member located in the extending direction of the first air flow channel, the first fixed seal member is combined with the first movable member to form a first control unit, wherein: The electromagnetic driving part and the first control part are connected and combined via a connecting piece to control the opening and closing of the first air flow channel.

7. The pressure regulating overflow device according to claim 5, wherein: The air supply pipeline and the exhaust pipeline in the exhaust valve constitute a second air flow channel, and further include: The electromagnetic drive unit is composed of an electromagnetic head, a valve core and an elastic component. A second fixed seal member located in the extending direction of the second air flow channel, the second fixed seal member is combined with a second movable member to form a second control unit, wherein: The electromagnetic drive unit and the second control unit are connected and combined via a connector to control the second movable member to produce a reciprocating stroke in the second air flow channel, and the exhaust valve selects the air supply pipeline and the exhaust pipeline.

8. The pressure regulating overflow device according to claim 7, wherein: The first branch also includes a pressure regulating valve, which is combined with a solenoid valve to form a first branch with controllable pipeline air pressure.

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