CN214367379U - Actuating system and commercial vehicle - Google Patents

Abstract

The utility model relates to a separation and reunion actuating system field of commercial car AMT gearbox specifically is an actuating system and a commercial car. The actuating system comprises a first flow limiting component with a pilot function and a linear actuator; the linear actuator comprises a shell and a piston, the inner cavity of the shell is divided into a pressurizing cavity and a breathing cavity by the piston, the pressurizing cavity and the breathing cavity are mutually isolated by the piston, and the pressurizing cavity and the breathing cavity can be respectively communicated with the atmosphere; the first flow limiting part is internally provided with a first short pipe joint flow passage, a second short pipe joint flow passage and a first mixing passage which can be selectively communicated. The first short pipe joint flow passage and the second short pipe joint flow passage are arranged in the first flow limiting part, so that the limited intervals of the first short pipe joint flow passage and the second short pipe joint flow passage can be set according to actual design requirements, and the control precision is higher.

Description

Actuating system and commercial vehicle

Technical Field

The utility model relates to a separation and reunion actuating system field of commercial car AMT gearbox specifically is an actuating system and a commercial car.

Background

Commercial vehicles (Commercial vehicles) are vehicles which are designed and technically designed to transport people and goods. The commercial vehicle comprises all cargo-carrying vehicles and passenger vehicles with more than 9 seats, and is divided into five types, namely a passenger vehicle, a freight vehicle, a semi-trailer tractor, a passenger vehicle incomplete vehicle and a freight vehicle incomplete vehicle.

An electric control mechanical automatic gearbox (AMT) is improved on the basis of a traditional manual gear type transmission, and is an electromechanical liquid integrated automatic transmission which integrates the advantages of AT (automatic) and MT (manual); the AMT has the advantages of automatic speed change of the hydraulic automatic transmission, and keeps the advantages of high efficiency, low cost, simple structure and easy manufacture of the original manual transmission gear transmission. Under the condition that the overall transmission structure of the mechanical gearbox is not changed, the automation of gear shifting is realized by additionally arranging an automatic control system controlled by a microcomputer. Therefore, the AMT actually performs the operation of operating the clutch and the gear selecting and shifting by an automatic gear shifting system.

Most commercial vehicles at present adopt a pneumatic braking system, compressed air generated by an engine driving an air compressor enters an oil-water separation device after being cooled to filter impurities (oil filtering, other impurities and the like) and dry gas, and finally the dry gas without the impurities is transmitted to an energy storage device (commonly called as an air storage cylinder) to be used as an air source of the pneumatic braking system.

In the prior art, a booster (application number: 201721905782.9) of a gas-assisted clutch is provided, wherein two fast electromagnetic valves and two slow electromagnetic valves are adopted, and an ECU controls the power-on or power-off of the fast electromagnetic valves and the slow electromagnetic valves to realize accurate control of a clutch position. It can be known from this prior art that the control of flow is carried out to the compressed air who pours into the helping hand cylinder body to adopt fast solenoid valve and slow solenoid valve to make the flow of the compressed air who pours into the helping hand cylinder body different.

In the prior art, the flow of compressed air injected into the boosting cylinder body is limited only by the electromagnetic valve, and the limited interval of the compressed air flow limited by the two electromagnetic valves with the similar models is relatively fixed, so that the air boosting clutch booster in the prior art has the technical problem of unsatisfactory control precision.

SUMMERY OF THE UTILITY MODEL

For solving among the prior art, only inject into the flow of the compressed air in the helping hand cylinder body through the solenoid valve restriction, the interval relatively fixed of the limit amount of two solenoid valve restriction compressed air flow that the model is close to make the gas power-assisted clutch booster among the prior art, there is the unsatisfactory technical problem of control accuracy, the utility model provides an actuating system and a commercial car.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

according to one aspect of the present invention, there is provided an actuator system comprising a first current limiting member having a pilot function and a linear actuator;

the linear actuator comprises a shell and a piston, the inner cavity of the shell is divided into a pressurization cavity and a breathing cavity by the piston, the pressurization cavity and the breathing cavity are mutually isolated by the piston, and the pressurization cavity and the breathing cavity can be respectively communicated with the atmosphere;

a first short pipe joint flow passage, a second short pipe joint flow passage and a first mixing passage which can be selectively communicated are arranged in the first flow limiting component, wherein the first short pipe joint flow passage, the second short pipe joint flow passage and the first mixing passage can respectively limit the flow of compressed air, and the first short pipe joint flow passage, the second short pipe joint flow passage and the first mixing passage can respectively be communicated with a pressurizing cavity; the flow limiting device comprises a first short pipe joint flow passage, a second short pipe joint flow passage, a first flow limiting device, a second flow limiting device and a second flow limiting device, wherein the flow limiting device comprises a first short pipe joint flow passage, the second short pipe joint flow passage and a second short pipe joint flow passage, the first short pipe joint flow passage is limited by the first short pipe joint flow passage, the second short pipe joint flow passage is limited by the second short pipe joint flow passage, the first flow is larger than or smaller than the second flow, and the first flow and the second flow are respectively larger than zero.

Further, the device also comprises a second current limiting component with a pilot function;

a third short pipe joint flow passage, a fourth short pipe joint flow passage and a second mixing passage which can be selectively communicated are arranged in the second flow limiting component, wherein the third short pipe joint flow passage, the fourth short pipe joint flow passage and the second mixing passage can respectively limit the flow of compressed air, the third short pipe joint flow passage, the fourth short pipe joint flow passage and the second mixing passage can be respectively communicated with the pressurizing cavity, the limiting flow of the third short pipe joint flow passage is a third flow, the limiting flow of the fourth short pipe joint flow passage is a fourth flow, the third flow is greater than or less than the fourth flow, and the third flow and the fourth flow are respectively greater than zero.

Further, the device also comprises an ECU and an angle sensor;

the angle sensor is provided with a resistance slideway and a sliding contact, and the sliding contact or the resistance slideway is electrically connected with the ECU.

Furthermore, the clutch device also comprises a swing rod arranged at the clutch device;

the linear actuator further comprises a guide rod, a first through hole is formed in the shell and is communicated with the breathing cavity, the first through hole and the piston are coaxially arranged, one end of the guide rod is arranged on the piston, and the other end of the guide rod penetrates through the first through hole;

the swing rod is provided with a central shaft which is in a rotatable state relative to the clutch device, wherein the extending direction of the swing rod and the axial direction of the central shaft are mutually crossed, one end of the swing rod is hinged to the guide rod, and the other end of the swing rod can contact the clutch device;

the angle sensor is coaxially connected with the central shaft, wherein the rotating angle of the sliding contact relative to the resistance slideway is the same as the swinging angle of the swinging rod.

Further, the linear actuator further comprises a spring and a lip seal;

the spring is arranged in the pressurizing cavity, wherein two ends of the spring are respectively connected to the shell and the piston;

the outer circumference of the piston is provided with the lip-shaped sealing ring, and dynamic sealing is formed between the piston and the inner wall of the shell through the lip-shaped sealing ring.

Further, the soft magnetic switch device comprises a first soft magnetic switch device, a second soft magnetic switch device, a third soft magnetic switch device and a fourth soft magnetic switch device;

the first soft magnetic switch device can be communicated with the first short pipe joint runner or the first mixing channel;

the second soft magnetic switch device can be communicated with the second short pipe joint runner or the first mixing channel;

the third soft magnetic switching device can be communicated with the third short pipe joint runner or the second mixing channel;

the fourth soft magnetic switching device may be in communication with the fourth stub flow channel or the second mixing channel.

Further, the electromagnetic valve also comprises a first electromagnetic coil, a second electromagnetic coil, a third electromagnetic coil and a fourth electromagnetic coil;

the first electromagnetic coil and the first soft magnetic switching device are correspondingly arranged, wherein the first soft magnetic switching device is positioned in a magnetic field generated by the first electromagnetic coil;

the second electromagnetic coil and the second soft magnetic switch device are correspondingly arranged, wherein the second soft magnetic switch device is positioned in the magnetic field generated by the second electromagnetic coil;

the third electromagnetic coil and the third soft magnetic switching device are correspondingly arranged, wherein the third soft magnetic switching device is positioned in a magnetic field generated by the third electromagnetic coil;

the fourth electromagnetic coil and the fourth soft magnetic switching device are arranged correspondingly, wherein the fourth soft magnetic switching device is positioned in a magnetic field generated by the fourth electromagnetic coil.

Further, the device also comprises a direct current power supply;

the direct current power supply is provided with a first output node, a second output node, a third output node and a fourth output node;

the first electromagnetic coil is electrically connected with the first output node;

the second electromagnetic coil is electrically connected with the second output node;

the third electromagnetic coil is electrically connected with the third output node;

the fourth electromagnetic coil is electrically connected with the fourth output node;

the ECU is electrically connected with the direct current power supply, wherein the ECU selectively switches on or off the first output node, the second output node, the third output node and the fourth output node.

Furthermore, the device also comprises a waterproof exhaust valve and an exhaust silencing valve;

a second through hole is formed in the shell, wherein the second through hole is communicated with the breathing cavity;

the waterproof exhaust valve is communicated with the second through hole, and the breathing cavity can be communicated with the atmosphere through the second through hole and the waterproof exhaust valve;

the third soft magnetic switch device and the fourth soft magnetic switch device are respectively communicated with the exhaust silencing valve through pipelines;

the exhaust silencing valve is communicated with the atmosphere.

According to another aspect of the present invention, a commercial vehicle is provided, comprising an execution system as described above.

The technical scheme has the following advantages or beneficial effects:

the utility model provides an actuating system is provided with first short tube coupling runner through first current-limiting component, and the short tube coupling runner of second can set up the interval of the limit of quantity of first short tube coupling runner and the short tube coupling runner of second according to the design requirement of reality, and control accuracy is higher.

Drawings

Fig. 1 is an electrical schematic diagram of an execution system according to an embodiment of the present invention;

fig. 2 is a schematic diagram of a gas circuit of an execution system provided in the embodiment of the present invention;

fig. 3 is a schematic circuit diagram of an execution system according to an embodiment of the present invention;

fig. 4 is a schematic diagram of a first current limiting component of an actuator system according to an embodiment of the present invention;

fig. 5 is a schematic diagram of a second current limiting component of an actuator system according to an embodiment of the present invention;

fig. 6 is a schematic diagram of a linear actuator of an actuator system according to an embodiment of the present invention;

fig. 7 is a schematic diagram of an angle sensor of an execution system according to an embodiment of the present invention;

fig. 8 is a schematic structural diagram of a part of an execution system according to an embodiment of the present invention.

Detailed Description

Referring to fig. 1, 2, 4 and 6, an actuator system comprises a first flow restriction member 1 having a pilot function and a linear actuator 2;

the linear actuator 2 comprises a shell 205 and a piston 201, the inner cavity of the shell 205 is divided into a pressure increasing cavity 202 and a breathing cavity 203 by the piston 201, the pressure increasing cavity 202 and the breathing cavity 203 are in a mutually isolated state through the piston 201, and the pressure increasing cavity 202 and the breathing cavity 203 can be respectively communicated with the atmosphere;

a first short pipe joint flow passage 101, a second short pipe joint flow passage 102 and a first mixing passage 103 which can be selectively communicated are arranged in the first flow limiting part 1, wherein the first short pipe joint flow passage 101, the second short pipe joint flow passage 102 and the first mixing passage 103 can limit the flow of compressed air respectively, and the first short pipe joint flow passage 101, the second short pipe joint flow passage 102 and the first mixing passage 103 can be communicated with a pressurizing cavity 202 respectively; the restricted flow of the first short pipe joint flow passage 101 is a first flow, the restricted flow of the second short pipe joint flow passage 102 is a second flow, the first flow is greater than or less than the second flow, and the first flow and the second flow are respectively greater than zero.

In the present embodiment, the pilot function is preferably a pneumatic pilot function, which is implemented by injecting compressed gas into the pilot structure to move the core relative to the housing of the first flow restriction member 1, and then resetting the core by the return spring 206. For example: a pilot-controlled valve device (application No. 201080052477.4) capable of multi-stage control is disclosed in the prior art.

In another embodiment, the first current limiting member 1 having an electromagnetic pilot function may be used, and the difference from the first current limiting member 1 having a pilot function described above is that the pilot function is implemented using an electromagnetic coil and an iron core. For example: the prior art discloses an electrically controlled pilot pneumatic valve (201910752237.8) for rail transit.

The two prior arts with pilot functions described above respectively include pilot structures for realizing the pilot functions, and the two pilot structures are respectively common knowledge known or should be known to those skilled in the art; that is, the first flow restriction member 1 having the pilot function is easily obtained by a person skilled in the art through common knowledge.

In the first flow restriction member 1 having the first position, the second position and the third position, in which the first mixing channel 103 is in the third position before the compressed air is injected into the first flow restriction member 1, and the first mixing channel 103 is in communication with the pressurizing chamber 202 of the linear actuator 2; when the compressed air in the first pipe 1001 is injected into the first flow restriction member 1, the first short pipe joint flow passage 101 moves from the first position to the third position, and communicates with the pressurizing chamber 202 of the linear actuator 2; when the compressed air in the second pipe 1002 is injected into the first flow restriction member 1, the second short pipe joint flow passage 102 moves from the second position to the third position, and communicates with the pressurizing chamber 202 of the linear actuator 2; when the compressed air in the first and second lines 1001 and 1002 is simultaneously injected into the first flow restriction member 1, the first mixing passage 103 is located at the third position, and the first mixing passage 103 communicates with the pressurizing chamber 202 of the linear actuator 2.

In the present embodiment, the first short pipe-section flow passage 101, the second short pipe-section flow passage 102, and the first mixing passage 103 are provided in common in the same first flow restriction member 1. The first short pipe joint flow channel 101 of the first flow limiting component 1 is used for conducting the compressed air from the first pipeline 1001 and limiting the flow rate of the compressed air to a first flow rate; the second short pipe segment flow passage 102 of the first flow restriction member 1 is used for conducting the compressed air from the second pipe 1002 and for restricting the flow rate of the compressed air to a second flow rate; since the first flow rate and the second flow rate are different, at least two kinds of pressurization speeds of the compressed air are formed in the process of injecting the compressed air into the pressurization cavity 202 of the linear actuator 2. And the first mixing passage 103 is used for simultaneously conducting the compressed air from the first pipe 1001 and the second pipe 1002, and the flow rate of the compressed air injected into the booster cavity 202 along the first mixing passage 103 is a first mixing flow rate, which may be greater than the sum of the first flow rate and the second flow rate, or may be less than the sum of the first flow rate and the second flow rate.

To facilitate understanding of those skilled in the art, the first short pipe joint flow passage 101 and the third short pipe joint flow passage 301 may be configured as a damping hole, and when the compressed air circulates in the damping hole, a pressure difference between both ends of the damping hole remains unchanged, but a flow rate of the compressed air discharged from the damping hole is reduced, thereby achieving an effect of limiting the flow rate of the compressed air. The first short pipe joint flow passage 101 and the second short pipe joint flow passage 102 in this embodiment may be respectively provided as damping holes with fixed apertures, so that the flow rate of the compressed air is limited, and the cost for manufacturing the first flow limiting member 1 can also be reduced.

The first mixing channel 103 may or may not be provided with a damping hole; if the damping hole is arranged, the effect that the first mixed flow is smaller than the sum of the first flow and the second flow can be realized, and if the damping hole is not arranged, the effect that the first mixed flow is larger than the sum of the first flow and the second flow can be realized; further, since it has been explained in the foregoing scheme that the first and second pipes 1001 and 1002 are connected to the first flow restriction member 1, respectively, and the first mixing passage 103 can communicate with the first and second pipes 1001 and 1002, respectively, two 'short pipe joint flow passages (orifice holes)' should be provided in the first mixing passage 103 under the condition that the first flow restriction member 1 is actually set such that the 'first mixed flow rate is smaller than the sum of the first and second flow rates', thereby enabling control of the precise restriction flow rate of the two compressed air paths.

If and only if the compressed air in the first pipe 1001 is injected into the first flow restriction member 1, the spool moves from the third position (current position) to the first position under the influence of the pneumatic pilot function and the compressed air, and at this time, the compressed air is injected into the pressurizing chamber 202 of the linear actuator 2 through the first short pipe joint flow passage 101.

If and only if the compressed air in the second pipe 1002 is injected into the first flow restriction member 1, the spool moves from the third position (current position) to the second position under the influence of the pneumatic pilot function and the compressed air, and at this time, the compressed air is injected into the pressurizing chamber 202 of the linear actuator 2 through the second short pipe joint flow passage 102.

When the compressed air in the first and second lines 1001 and 1002 is simultaneously injected into the first flow restriction member 1, the spool is held at the third position (current position) by the pneumatic pilot function and the compressed air, and at this time, the compressed air is injected into the pressurizing chamber 202 of the linear actuator 2 through the first mixing passage 103.

In the prior art, the flow of the compressed air injected into the boosting cylinder body is limited only by the electromagnetic valve, and as the valve core channel calibers of the electromagnetic valves are single, and the difference between the valve core channel calibers of two electromagnetic valves with similar models is large, when the electromagnetic valve is actually used as a 'flow limiting component', the limited interval formed by the two electromagnetic valves is relatively fixed, and the control precision is low. For example: the valve core outlets of two electromagnetic valves with similar models are a quarter valve and a sixth branch valve respectively, but the valve core outlets of the electromagnetic valves in the prior art do not have a quarter-half valve and a third-half valve or a fifth branch valve and a seventh branch valve and the like.

In the execution system provided by this embodiment, the first short pipe joint flow passage 101 and the second short pipe joint flow passage 102 are provided in the first flow limiting part 1, so that the limited intervals of the first short pipe joint flow passage 101 and the second short pipe joint flow passage 102 can be set according to the actual design requirements, and the control accuracy is higher. For example, the spool outlet of the first short-tube-section flow passage 101 may be set to quarter or half, or the spool outlet of the second short-tube-section flow passage 102 may be set to fifth or seventh, or the like.

On the basis of the first short pipe joint flow passage 101 and the second short pipe joint flow passage 102, the 'short pipe joint flow passage' may be provided or may not be provided in the first mixing cavity of the first flow restriction member 1, so that the execution system of the present embodiment has at least three ways of restricting the flow rate of the compressed air. If two electromagnetic valves with different types are opened simultaneously in the prior art, the flow of the compressed air injected into the boosting cylinder body is the sum of the two paths of compressed air flows; however, in this embodiment, if the 'short tube joint flow channel' is not provided in the first mixing cavity channel, the flow rate of the compressed air injected into the mixing cavity may be greater than the sum of the two compressed air channels, whereas if the 'short tube joint flow channel' is provided in the first mixing cavity, the flow rate of the compressed air injected into the mixing cavity may be less than the sum of the two compressed air channels, that is, the first mixing channel 103 may limit the sum of the two compressed air channels to different flow rates, so that the implementation system of this embodiment obtains the effect of limiting the compressed air flow rate in a wider range compared with the prior art.

Further, in the present embodiment, referring to fig. 1, 2, 5 and 6, a second flow restriction part 3 having a pilot function is further included;

a third short pipe joint flow passage 301, a fourth short pipe joint flow passage 302 and a second mixing passage 303 which can be selectively communicated are arranged in the second flow limiting component 3, wherein the third short pipe joint flow passage 301, the fourth short pipe joint flow passage 302 and the second mixing passage 303 can respectively limit the flow of compressed air, the third short pipe joint flow passage 301, the fourth short pipe joint flow passage 302 and the second mixing passage 303 can be respectively communicated with the pressurizing cavity 202, the limiting flow of the third short pipe joint flow passage 301 is a third flow, the limiting flow of the fourth short pipe joint flow passage 302 is a fourth flow, the third flow is greater than or less than the fourth flow, and the third flow and the fourth flow are respectively greater than zero.

The structure of the second flow restriction component 3 is the same as that of the first flow restriction component 1, and the effect of the second flow restriction component 3 is similar to that of the first flow restriction component 1, and the difference between the two is only: the first flow restriction member 1 acts on the process of injecting compressed air into the pressurizing chamber 202 of the linear actuator 2, and the second flow restriction member 3 acts on the process of discharging compressed air from the pressurizing chamber 202 of the linear actuator 2. The detailed structure and effect of the second flow restriction member 3 will not be described herein.

The third short-pipe joint flow passage 301 of the second restrictor 3 communicates with the pressure increasing chamber 202 of the linear actuator 2 via a third line 1003, and the fourth short-pipe joint flow passage 302 communicates with the pressure increasing chamber 202 of the linear actuator 2 via a fourth line 1004.

If and only if the compressed air in the pressurizing chamber 202 is discharged through the third line 1003, the spool moves from the third position (current position) to the first position by the influence of the pneumatic pilot function and the compressed air, and at this time, the compressed air is discharged out of the pressurizing chamber 202 through the third short pipe joint flow passage 301.

If and only if the compressed air in the booster chamber 202 is discharged through the fourth pipe 1004, the spool moves from the third position (current position) to the second position under the influence of the pneumatic pilot function and the compressed air, and at this time, the compressed air is discharged out of the booster chamber 202 through the fourth short pipe joint flow passage 302.

When the compressed air in the pressurizing chamber 202 is simultaneously discharged through the third line 1003 and the fourth line 1004, the spool is held at the third position (current position) by the influence of the pneumatic pilot function and the compressed air, and at this time, the compressed air is discharged out of the pressurizing chamber 202 through the second mixing passage 303.

Further, in the present embodiment, referring to fig. 1, 2 and 7, an ECU6 and an angle sensor 9 are further included;

the angle sensor 9 has a resistive slide 901 and a sliding contact 902, and the sliding contact 902 or the resistive slide 901 is electrically connected to the ECU 6.

An Electronic Control Unit (ECU) 6(Electronic Control Unit) ECU6 is composed of a Microprocessor (MCU), a memory (ROM, RAM), an input/output interface (I/O), an analog-to-digital converter (a/D), and a large-scale integrated circuit such as a shaping circuit and a driving circuit, as in a general computer.

It should be understood that the ECU6 in the present embodiment may be the ECU6-1 of the transmission, or the ECU6-2 of the engine, or the ECU6-3 of the brake system, etc.; or may be the ECU6 integrated on a chip module having a power supply.

The angle sensor 9 has a resistive slide 901 and a sliding contact 902. The angle sensor 9 may have the following structure: the slider 902 is swingable with respect to the sensor housing 205 of the angle sensor 9, while the resistive slide 901 is fixed with respect to the sensor housing 205 of the angle sensor 9.

The angle sensor 9 is used for detecting the moving direction and the moving distance of the piston 201 of the linear actuator 2, so that a feedback electric signal for monitoring the displacement of the piston 201 can be generated, and the feedback electric signal can be fed back to the ECU6, so that the ECU6 and the angle sensor 9 are combined with a closed-loop control system to realize a closed-loop control function of the execution control mechanism of the embodiment.

In the prior art (an air-assisted clutch booster, application No. 201721905782.9) proposed in the background art, the displacement sensor itself has a relatively large number of electromagnetic coils, and thus is relatively expensive.

In this embodiment, the circuit structure of the angle sensor 9 is very simple, and the angle sensor can be implemented by the resistor chute 901 and the sliding contact 902 without the electromagnetic coil, thereby reducing the cost of the execution control mechanism.

In the aforementioned prior art (an air-assisted clutch booster, application No. 201721905782.9), the measurement object of the displacement sensor is a sensor core which can penetrate through the coil of the solenoid valve, as seen from the text and drawings; as the compressed air inevitably contains water vapor, the water vapor or condensed water inevitably reaches the electromagnetic coil through the movement of the sensor iron core in the process of detecting the sensor iron core by the displacement sensor, so that the electromagnetic coil is short-circuited.

In the present embodiment, the sensor core is not provided, so that the phenomenon that the electromagnetic coil is short-circuited due to the inevitable movement of water vapor or condensed water to the electromagnetic coil by the sensor core in the prior art (a gas-assisted clutch booster, application number: 201721905782.9) does not occur.

Specifically, referring to fig. 1, 2, 6 and 8, a swing link 8 disposed at the clutch device 100 is further included;

the linear actuator 2 further comprises a guide rod 204, a first through hole 207 is formed in the housing 205, the first through hole 207 is communicated with the breathing cavity 203, the first through hole 207 and the piston 201 are coaxially arranged, one end of the guide rod 204 is arranged on the piston 201, and the other end of the guide rod 204 penetrates through the first through hole 207;

the oscillating bar 8 is provided with a central shaft 801, the central shaft 801 is in a rotatable state relative to the clutch device 100, wherein the extending direction of the oscillating bar 8 and the axial direction of the central shaft 801 are mutually crossed, one end of the oscillating bar 8 is hinged to the guide rod 204, and the other end of the oscillating bar 8 can contact the clutch device 100;

the angle sensor 9 is connected coaxially to the central shaft 801, wherein the angle of rotation of the sliding contact 902 relative to the resistive track 901 is the same as the angle of oscillation of the rocker 8.

In this case, the swing link 8 may be actually disposed at the clutch device 100 through a cam, or the swing link 8 may be disposed at the clutch device 100 through a pair of support plates having shaft holes. One end of the oscillating bar 8 is hinged with the guide rod 204, and the other end of the oscillating bar 8 can contact with the clutch device 100. One end of the guide rod 204 is connected to the piston 201.

When the angle sensor 9 is disposed on the swing link 8, the sliding contact 902 and the swing link 8 are coaxially connected and can rotate in the same direction, and the swing angular velocity of the sliding contact 902 is the same as the swing angular velocity of the swing link 8.

When the piston 201 in the linear actuator 2 moves along the direction from the pressurization cavity 202 to the breathing cavity 203 and the piston 201 moves along the direction from the breathing cavity 203 to the pressurization cavity 202, the guide rod 204 is in a reciprocating state, and the angle sensor 9 can obtain the moving direction and the moving distance of the piston 201 through the swing rod 8 hinged to the guide rod 204, so as to generate a feedback electric signal for monitoring the displacement of the piston 201.

It should be understood that in the prior art, for example: a gas-assisted clutch booster (application number: 201721905782.9) adopts a displacement sensor to measure the displacement of a sensor iron core (corresponding to a piston 201 in the embodiment) of the clutch booster; from the figures of the prior art, it is evident that in the area of action of the air pressure of the cylinder (corresponding to the pressurization chamber 202 of the present embodiment), the actuator cylinder of which is provided with an opening through which the sensor core can penetrate, this results in the sensor core occupying the active area of the cylinder, which is: the difference between the area of the radial cross section of the cylinder and the area of the opening.

In the present embodiment, the piston 201 is disposed inside the housing 205 (corresponding to a cylinder in the prior art), and the pressurizing chamber 202 between the piston 201 and the housing 205 does not have the opening in the prior art (an air-assisted clutch booster, application No. 201721905782.9), so that the effective area of the housing 205 is the area of the radial interface of the housing 205 in the present embodiment. With the same volume of the cylinder (housing 205), compared with the prior art (a gas-assisted clutch booster, application number: 201721905782.9), the housing 205 in this embodiment has a smaller opening, so as to increase the work efficiency of the air pressure in the pressurizing cavity 202, that is, the work efficiency of the 'cylinder structure' formed by the housing 205 and the piston 201 in this embodiment is higher.

In the aforementioned prior art (a gas-assisted clutch booster, application No. 201721905782.9), a separate cover is provided between the solenoid valve and the cylinder, and the cover is used to cover the aforementioned opening, thereby providing a structural basis for sealing the opening on the solenoid valve side, fixing the displacement sensor, and the like. This results in an increase in the actual volume of the prior art (a gas-assisted clutch booster, application No. 201721905782.9) and, in practical use, an increase in the weight of the actuator.

In this embodiment, the angle sensor 9 is disposed at a position away from the housing 205, and the base structure for fixing the angle sensor 9 may be a structure other than the housing 205, so that the number of the independent cover body can be reduced compared to the aforementioned prior art (a gas-assisted clutch booster, application No. 201721905782.9), and the volume and weight of the actuator control mechanism can be reduced.

In the aforementioned prior art (a gas-assisted clutch booster, application No. 201721905782.9), as seen from the overall specification and drawings, a plurality of solenoid valves are provided in the vicinity of the displacement sensor, which enables a magnetic field generated by a coil of the displacement sensor to interfere with the magnetic fields of the plurality of solenoid valves, and an electromagnetic armature of the solenoid valve moves eccentrically during the movement process, so that the electromagnetic armature is worn, and the service life of the solenoid valve is finally reduced. And, because the electromagnetic valve and the displacement sensor are close to each other, in order to avoid the situation that electromagnetic fields interfere with each other, a safety interval must be adopted from the technical point of view, thereby increasing the volume and occupied space of the prior art (a gas-assisted clutch booster, application number: 201721905782.9).

In the embodiment, the angle sensor 9 is far away from the solenoid valve or similar electromagnetic structure, so that the problem that the magnetic field generated by the coil of the displacement sensor can interfere with the magnetic fields of a plurality of solenoid valves, and the electromagnetic armature of the solenoid valve eccentrically moves in the moving process to cause abrasion of the electromagnetic armature, thereby finally reducing the service life of the solenoid valve, which is shown in the prior art (an air-assisted clutch booster, application number: 201721905782.9) is solved. Also, a safety gap is no longer required, thereby making the linear control mechanism of this embodiment less bulky or taking up space.

Further, in the present embodiment, referring to fig. 6, the linear actuator 2 further includes a spring 206 and a lip seal 208;

a spring 206 is disposed in the pressurizing chamber 202, wherein both ends of the spring 206 are connected to the housing 205 and the piston 201, respectively;

a lip-shaped sealing ring 208 is arranged on the outer circumference of the piston 201, and dynamic sealing is formed between the piston 201 and the inner wall of the shell 205 through the lip-shaped sealing ring 208.

One end of the guide rod 204 is disposed in the breathing cavity 203 of the housing 205 through the first through hole 207 and coaxially connected to the piston 201, and the other end of the guide rod 204 is disposed outside the housing 205 and hinged to one end of the swing rod 8.

A spring 206 (see fig. 6) is provided in the pressurizing chamber 202 or the breathing chamber 203 of the linear actuator 2, and both ends of the spring 206 are connected to the piston 201 and the housing 205, respectively.

Under the action of compressed air injected by the first flow limiting component 1, the air pressure in the pressurization cavity 202 in the housing 205 is gradually increased, and according to the pascal principle, when the air pressure in the pressurization cavity 202 is greater than the air pressure in the breathing cavity 203, the piston 201 moves along the direction from the pressurization cavity 202 to the breathing cavity 203, so that the guide rod 204 is driven to move along the direction from the linear actuator 2 to the swing rod 8, and at the moment, the spring 206 is changed from a contraction state to a stretching state in the breathing cavity 203; on the contrary, when the compressed air in the pressurizing cavity 202 is exhausted through the second flow restriction component 3, the piston 201 has a tendency to change from the stretching state to the contracting state in the spring 206, and a pulling force exerted on the piston 201 by the spring 206 is formed, so that the piston 201 is forced to move along the direction from the breathing cavity 203 to the pressurizing cavity 202.

A gap is provided between the circumferential portion of the piston 201 and the inner wall of the housing 205, and a lip-shaped seal ring 208 is provided on the circumferential portion of the piston 201 in order to prevent the compressed air in the pressurizing chamber 202 from being injected into the breathing chamber 203 through the gap; a gap between the circumferential portion of the piston 201 and the inner wall of the housing 205 is sealed by a lip seal 208.

Further, in the present embodiment, referring to fig. 1 to 5, a first soft magnetic switching device 401, a second soft magnetic switching device 402, a third soft magnetic switching device 403, and a fourth soft magnetic switching device 404 are further included;

the first soft magnetic switching device 401 may be connected to the first stub pipe flow channel 101 or the first mixing channel 103;

the second soft magnetic switching device 402 can be communicated with the second short pipe joint runner 102 or the first mixing channel 103;

the third soft magnetic switch device 403 can be communicated with the third short pipe joint runner 301 or the second mixing channel 303;

the fourth soft magnetic switching device 404 may be in communication with the fourth stub pipe flow channel 302 or the second mixing channel 303.

It should be understood that in the present embodiment, the first soft magnetic switching device 401, the second soft magnetic switching device 402, the third soft magnetic switching device 403 and the fourth soft magnetic switching device 404 may be independent switching devices without an electric control structure.

In other embodiments, the first soft magnetic switch device 401, the second soft magnetic switch device 402, the third soft magnetic switch device 403, and the fourth soft magnetic switch device 404 may also be part of a solenoid valve, for example, including at least a valve body of the solenoid valve and a valve core structure made of soft magnetic material.

The first soft magnetic switching device 401, the second soft magnetic switching device 402, the third soft magnetic switching device 403, and the fourth soft magnetic switching device 404 in this embodiment are normally closed 'switching elements', respectively.

Since the aforementioned first flow restriction member 1 has the first mixing passage 103 and the second flow restriction member 3 has the second mixing passage 303, the compressed air can directly discharge the first flow restriction member 1 from the first mixing passage 103 and the compressed air can directly discharge the second flow restriction member 3 from the second mixing passage 303. Therefore, the first and second flow restricting parts 1 and 3 do not have the shut-off function of the 'valve'.

The first soft magnetic switch device 401 and the second soft magnetic switch device 402 are respectively communicated with the first current limiting component 1 through pipelines, so that the first current limiting component 1 has a 'valve' cutoff function through the first soft magnetic switch device 401 and the second soft magnetic switch device 402.

Similarly, the third soft magnetic switch device 403 and the fourth soft magnetic switch device 404 are connected to the second flow limiting component 3 through a pipeline, so that the third discharge port has a valve cutoff function through the third soft magnetic switch device 403 and the fourth soft magnetic switch device 404.

Further, in the present embodiment, referring to fig. 1 to 3, a first electromagnetic coil 501, a second electromagnetic coil 502, a third electromagnetic coil 503, and a fourth electromagnetic coil 504 are further included;

the first electromagnetic coil 501 and the first soft magnetic switching device 401 are arranged correspondingly, wherein the first soft magnetic switching device 401 is positioned in a magnetic field generated by the first electromagnetic coil 501;

the second electromagnetic coil 502 and the second soft magnetic switching device 402 are correspondingly arranged, wherein the second soft magnetic switching device 402 is positioned in the magnetic field generated by the second electromagnetic coil 502;

the third electromagnetic coil 503 and the third soft magnetic switch device 403 are correspondingly arranged, wherein the third soft magnetic switch device 403 is positioned in the magnetic field generated by the third electromagnetic coil 503;

the fourth electromagnetic coil 504 is disposed in correspondence with the fourth soft magnetic switching device 404, wherein the fourth soft magnetic switching device 404 is located within the magnetic field generated by the fourth electromagnetic coil 504.

The first soft magnetic switching device 401, the second soft magnetic switching device 402, the third soft magnetic switching device 403, and the fourth soft magnetic switching device 404 described above do not have an electric control structure in this embodiment.

By adopting the first electromagnetic coil 501 and the first soft magnetic switch device 401, when the first electromagnetic coil 501 is powered on, the first electromagnetic coil 501 generates a first magnetic field, the first soft magnetic switch device 401 located in the first magnetic field is changed from a cut-off state to a conducting state, and when the first electromagnetic coil 501 is powered off, the first magnetic field disappears, and the first soft magnetic switch device 401 is changed from the conducting state to the cut-off state.

Similarly, the usage effects of the second electromagnetic coil 502, the third electromagnetic coil 503 and the fourth electromagnetic coil 504 are respectively the same as the usage effects of the first electromagnetic coil 501, and are not described herein.

It will be appreciated that soft magnetic switching devices are one type of prior art magnetic valves, for example: a perpendicular magnetization spin valve with a nano-soft magnetic core is provided in the prior art (application No. 201010153452.5) and a bistable microvalve (201010219061.9) is provided in the prior art, wherein a valve structure with soft magnetic material is provided separately. That is, soft magnetic switches are common knowledge known or should be known to those skilled in the art.

Further, in the present embodiment, referring to fig. 1 and fig. 3, the power supply further includes a dc power supply 7;

the direct-current power supply 7 is provided with a first output node 701, a second output node 702, a third output node 703 and a fourth output node 704;

the first electromagnetic coil is electrically connected with the first output node 701;

the second electromagnetic coil is electrically connected to the second output node 702;

the third electromagnetic coil is electrically connected to the third output node 703;

the fourth electromagnetic coil is electrically connected with the fourth output node 704;

the ECU6 is electrically connected to the dc power supply 7, wherein the ECU6 selectively turns on or off the first output node 701, the second output node 702, the third output node 703 and the fourth output node 704.

The first output node 701, the second output node 702, the third output node 703 and the fourth output node 704 of the dc power supply 7 are respectively configured to output PWM pulse width signals. The PWM pulse width signal is specifically: various Pulse Width Modulation (PWM) techniques include: the pulse width PWM method is that pulse trains with equal pulse width are used as PWM waveforms, frequency modulation can be performed by changing the period of the pulse trains, voltage regulation can be performed by changing the width or duty ratio of the pulses, and the voltage and the frequency can be changed coordinately by adopting a proper control method. The purpose of controlling the charging current can be achieved by adjusting the period of PWM and the duty ratio of PWM.

The ECU6 may control the on/off states of the first output node 701, the second output node 702, the third output node 703 and the fourth output node 704 on the dc power supply 7, thereby realizing an alternative output PWM pulse width signal to control the aforementioned energization or deenergization of the first electromagnetic coil, the second electromagnetic coil, the third electromagnetic coil and the fourth electromagnetic coil.

Further, in the embodiment, referring to fig. 1 and fig. 2, a waterproof exhaust valve 10 is further included;

a second through hole 209 is formed in the housing 205, wherein the second through hole 209 is communicated with the breathing cavity 203;

the waterproof exhaust valve 10 is communicated with the second through hole 209, and the breathing cavity 203 can be communicated with the atmosphere through the second through hole 209 and the waterproof exhaust valve 10.

The breathing cavity 203 is communicated with the atmosphere through the second through hole 209, wherein during the aforementioned movement of the piston 201 relative to the housing 205, if the piston 201 moves along the direction from the pressurization cavity 202 to the breathing cavity 203, the air in the breathing cavity 203 is exhausted to the atmosphere through the second through hole 209; on the contrary, if the piston 201 moves along the direction from the breathing chamber 203 to the pressurizing chamber 202, air in the atmosphere can be injected into the breathing chamber 203 through the second through hole 209.

If the execution system of the embodiment is actually arranged on a commercial vehicle, the linear actuator 2 is actually arranged at the bottom of the AMT gearbox, that is, the distance between the second through hole 209 of the linear actuator 2 and the ground is smaller than the distance between the AMT gearbox and the ground; with this arrangement, if the commercial vehicle is driven on a complicated road surface, for example: a sand road with a puddle, water and sand may be injected into the breathing chamber 203 through the second through hole 209. Therefore, after the waterproof exhaust valve 10 is disposed on the second through hole 209, water and sand can be prevented from being injected into the breathing cavity 203 through the second through hole 209.

Further, in the present embodiment, referring to fig. 1 and 2, an exhaust muffler valve 11 is further included;

the third soft magnetic switch device 403 and the fourth soft magnetic switch device 404 are respectively communicated with the exhaust silencing valve 11 through pipelines;

the exhaust muffler valve 11 is open to the atmosphere.

By providing the exhaust muffler valve 11, noise in the pressurizing chamber 202 during exhaust can be reduced.

On the basis of all the schemes, when the execution system is actually applied to an AMT gearbox system of a commercial vehicle, the air circuit of the execution system is connected with an air source of the commercial vehicle, and the circuit of the execution system is electrically connected with the ECU 6.

For example: the commercial vehicle is provided with an air compressor and an air storage tank, and the execution system is communicated with the air storage tank through a pipeline; the air storage tank stores compressed air produced by the air compressor and conveys the compressed air to the direction of the first flow limiting component 1 through a pipeline.

When the execution system of the embodiment works, the control purpose is to make the linear actuator 2 perform the telescopic action, so that the guide rod 204 on the linear actuator can drive the clutch to generate the combining action and the separating action. Wherein, the ECU6 receives a first control signal of the commercial vehicle, the ECU6 system program outputs a first action signal for controlling the dc power supply 7 according to the first control signal, so that the first output node 701 of the dc power supply 7 is in a conducting state and outputs a first PWM pulse width signal to the first electromagnetic coil 501, and the first electromagnetic coil 501 generates a magnetic field to make the first soft magnetic switch change from a cut-off state to a conducting state; at this time, compressed air is injected from the air tank into the first flow restriction member 1, and after the flow rate is restricted by the first short pipe joint flow passage 101, the compressed air is injected into the booster cavity 202 of the linear actuator 2; alternatively, the ECU6 system program outputs a second control signal for controlling the dc power supply 7 according to the first control signal, the second output node 702 of the dc power supply 7 is turned on and outputs a second PWM pulse width signal to the second electromagnetic coil 502, and the second electromagnetic coil 502 generates a magnetic field to change the second soft magnetic switch from the off state to the on state; at this time, compressed air is injected from the air tank into the first flow restriction member 1, and after the flow rate is restricted by the second short pipe joint flow passage 102, the compressed air is injected into the booster cavity 202 of the linear actuator 2; because the first short pipe joint flow channel 101 and the second short pipe joint flow channel 102 of the first flow limiting component 1 have different limiting flow rates, if and only if one of the first soft magnetic switch and the second soft magnetic switch is in a conducting state, under the action of the pilot function of the first flow limiting component 1, if the limiting flow rate of the first short pipe joint flow channel 101 is greater than the limiting flow rate of the second short pipe joint flow channel 102, the time for converting air pressure energy into mechanical energy is shorter when compressed air output by the first short pipe joint flow channel 101 is obtained in the pressurizing cavity 202, which results in that the speed for the piston 201 to push the guide rod 204 is faster, and correspondingly, when compressed air output by the second short pipe joint flow channel 102 is obtained in the pressurizing cavity 202, the time for converting air pressure energy into mechanical energy is longer, which results in that the speed for the piston 201 to push the guide rod 204 is slower; when the first soft magnetic switch and the second soft magnetic switch are in the conducting state at the same time, under the action of the pilot function of the first current limiting component 1, the compressed air output by the first mixing channel 103 is available in the pressure increasing cavity 202, so that the time for converting the air pressure energy into the mechanical energy is shorter (for example, no short pipe throttling channel is provided in the first mixing channel 103) or longer (for example, two or more short pipe throttling channels are provided in the first mixing channel 103), resulting in that the piston 201 pushes the guide rod 204 faster or slower.

Conversely, when the ECU6 receives the second control signal of the commercial vehicle, the ECU6 system program outputs the third operation signal and/or the fourth control signal for controlling the dc power supply 7 according to the second control signal, the third output node 703 and/or the fourth output node 704 of the dc power supply 7 are/is turned on and outputs the third PWM pulse width signal to the third electromagnetic coil 503 or outputs the fourth PWM pulse width signal to the fourth electromagnetic coil 504, and the third electromagnetic coil 503 generates a magnetic field to turn the third soft magnetic switch from the off state to the on state, or the fourth electromagnetic coil 504 generates a magnetic field to turn the fourth soft magnetic switch from the off state to the on state; at this time, the compressed air is discharged from the inside of the pressurizing chamber 202 of the linear actuator 2 to the second flow restriction member 3; because the third short pipe joint flow passage 301 and the fourth short pipe joint flow passage 302 of the first flow restriction component 1 have different flow restriction rates, if and only if one of the third soft magnetic switch and the fourth soft magnetic switch is in a conducting state, under the action of the pilot function of the second flow restriction component 3, if the flow restriction rate of the third short pipe joint flow passage 301 is greater than the flow restriction rate of the fourth short pipe joint flow passage 302, the discharge time of the compressed air in the pressurizing cavity 202 along the third short pipe joint flow passage 301 is relatively short, which results in a relatively fast speed of the piston 201 returning to the original position under the action of the spring 206, and correspondingly, the discharge time of the compressed air in the pressurizing cavity 202 along the fourth short pipe joint flow passage 302 is relatively long, which results in a relatively slow speed of the piston 201 returning to the original position under the action of the spring 206; when the third soft magnetic switch and the fourth soft magnetic switch are in the on state at the same time, under the action of the pilot function of the second current limiting component 3, the compressed air in the booster cavity 202 can be discharged through the second mixing channel 303, so that the discharge speed of the compressed air in the booster cavity 202 is faster (for example, no short pipe section flow channel is provided in the third mixing channel) or slower (for example, two or more short pipe section flow channels are provided in the second mixing channel 303 respectively), which results in that the speed of the piston 201 returning to the original position under the action of the spring 206 is faster or slower.

In this embodiment, a commercial vehicle is further provided, which includes the above-mentioned execution system. The commercial vehicle is provided with the execution system, so that the specific effect of the scheme of the commercial vehicle comprises the specific effect of the execution system, which is not described herein again.

The above only is the preferred embodiment of the present invention, not limiting the scope of the present invention, all the equivalent structural changes made by the contents of the specification and the drawings, or the direct or indirect application in other related technical fields, are included in the same way in the protection scope of the present invention.

Claims (10)

1. An actuator system, characterized by comprising a first flow restriction member (1) having a pilot function and a linear actuator (2);

the linear actuator (2) comprises a shell (205) and a piston (201), the inner cavity of the shell (205) is divided into a pressurization cavity (202) and a breathing cavity (203) by the piston (201), the pressurization cavity (202) and the breathing cavity (203) are in a mutually isolated state through the piston (201), and the pressurization cavity (202) and the breathing cavity (203) can be respectively communicated with the atmosphere;

a first short pipe joint flow passage (101), a second short pipe joint flow passage (102) and a first mixing channel (103) which can be selectively communicated are arranged in the first flow limiting component (1), wherein the first short pipe joint flow passage (101), the second short pipe joint flow passage (102) and the first mixing channel (103) can limit the flow of compressed air respectively, and the first short pipe joint flow passage (101), the second short pipe joint flow passage (102) and the first mixing channel (103) can be communicated with a pressurizing cavity (202) respectively; the flow limiting rate of the first short pipe joint flow passage (101) is a first flow rate, the flow limiting rate of the second short pipe joint flow passage (102) is a second flow rate, the first flow rate is greater than or less than the second flow rate, and the first flow rate and the second flow rate are respectively greater than zero.

2. The actuator system according to claim 1, further comprising a second flow restriction member (3) having a pilot function;

a third short pipe joint flow passage (301), a fourth short pipe joint flow passage (302) and a second mixing passage (303) which can be selectively communicated are arranged in the second flow limiting component (3), wherein the third short pipe joint flow passage (301), the fourth short pipe joint flow passage (302) and the second mixing passage (303) can respectively limit the flow of compressed air, the third short pipe joint flow passage (301), the fourth short pipe joint flow passage (302) and the second mixing passage (303) can be respectively communicated with the pressurizing cavity (202), the limiting flow of the third short pipe joint flow passage (301) is a third flow, the limiting flow of the fourth short pipe joint flow passage (302) is a fourth flow, the third flow is greater than or less than the fourth flow, and the third flow and the fourth flow are respectively greater than zero.

3. The execution system of claim 2, further comprising an ECU (6) and an angle sensor (9);

the angle sensor (9) is provided with a resistance slide way (901) and a sliding contact (902), and the sliding contact (902) or the resistance slide way (901) is electrically connected with the ECU (6).

4. Actuator system according to claim 3, further comprising a rocker (8) arranged at the clutch device (100);

the linear actuator (2) further comprises a guide rod (204), a first through hole (207) is formed in the shell (205), the first through hole (207) is communicated with the breathing cavity (203), the first through hole (207) and the piston (201) are coaxially arranged, one end of the guide rod (204) is arranged on the piston (201), and the other end of the guide rod (204) penetrates through the first through hole (207);

a central shaft (801) is arranged on the swing rod (8), the central shaft (801) is in a rotatable state relative to the clutch device (100), the extending direction of the swing rod (8) and the axial direction of the central shaft (801) are mutually crossed, one end of the swing rod (8) is hinged to the guide rod (204), and the other end of the swing rod (8) can contact the clutch device (100);

the angle sensor (9) is coaxially connected with the central shaft (801), wherein the rotating angle of the sliding contact (902) relative to the resistance slideway (901) is the same as the swinging angle of the swinging rod (8).

5. The actuation system according to claim 1, characterized in that the linear actuator (2) further comprises a spring (206) and a lip seal (208);

the spring (206) is arranged in the pressurization cavity (202), wherein two ends of the spring (206) are respectively connected to the shell (205) and the piston (201);

the outer circumference of the piston (201) is provided with the lip-shaped sealing ring (208), and dynamic sealing is formed between the piston (201) and the inner wall of the shell (205) through the lip-shaped sealing ring (208).

6. Actuator system according to claim 3, further comprising a first soft magnetic switching device (401), a second soft magnetic switching device (402), a third soft magnetic switching device (403) and a fourth soft magnetic switching device (404);

the first soft magnetic switch device (401) can be communicated with the first short pipe joint runner (101) or the first mixing channel (103);

the second soft magnetic switch device (402) can be communicated with the second short pipe joint runner (102) or the first mixing channel (103);

the third soft magnetic switch device (403) can be communicated with the third short pipe joint flow channel (301) or the second mixing channel (303);

the fourth soft magnetic switching device (404) may be in communication with the fourth stub pipe flow channel (302) or the second mixing channel (303).

7. The actuator system according to claim 6, further comprising a first solenoid coil (501), a second solenoid coil (502), a third solenoid coil (503), and a fourth solenoid coil (504);

the first electromagnetic coil (501) and the first soft magnetic switching device (401) are arranged correspondingly, wherein the first soft magnetic switching device (401) is located in a magnetic field generated by the first electromagnetic coil (501);

the second electromagnetic coil (502) and the second soft magnetic switching device (402) are arranged correspondingly, wherein the second soft magnetic switching device (402) is positioned in a magnetic field generated by the second electromagnetic coil (502);

the third electromagnetic coil (503) and the third soft magnetic switching device (403) are arranged correspondingly, wherein the third soft magnetic switching device (403) is positioned in a magnetic field generated by the third electromagnetic coil (503);

the fourth electromagnetic coil (504) and the fourth soft magnetic switching device (404) are arranged correspondingly, wherein the fourth soft magnetic switching device (404) is positioned in a magnetic field generated by the fourth electromagnetic coil (504).

8. The execution system of claim 7, further comprising a direct current power supply (7);

the direct current power supply (7) is provided with a first output node (701), a second output node (702), a third output node (703) and a fourth output node (704);

the first electromagnetic coil (501) is electrically connected with the first output node (701);

the second electromagnetic coil (502) is electrically connected to the second output node (702);

the third electromagnetic coil (503) is electrically connected with the third output node (703);

said fourth electromagnetic coil (504) and said fourth output node (704) being electrically connected;

the ECU (6) is electrically connected with the direct current power supply (7), wherein the ECU (6) can selectively turn on or off the first output node (701), the second output node (702), the third output node (703) and the fourth output node (704).

9. The actuator system according to claim 7, further comprising a waterproof exhaust valve (10) and an exhaust silencing valve (11);

a second through hole (209) is formed in the shell (205), wherein the second through hole (209) is communicated with the breathing cavity (203);

the waterproof exhaust valve (10) is communicated with the second through hole (209), and the breathing cavity (203) can be communicated with the atmosphere through the second through hole (209) and the waterproof exhaust valve (10);

the third soft magnetic switch device (403) and the fourth soft magnetic switch device (404) are respectively communicated with the exhaust silencing valve (11) through pipelines;

the exhaust silencing valve (11) is communicated with the atmosphere.

10. A commercial vehicle, characterized in that it comprises an execution system according to any one of claims 1 to 9.

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