Magnetorheological shock absorber and control system and method therefor, vehicle, device, and medium

Abstract

The present invention relates to the technical field of vehicles. Disclosed are a magnetorheological shock absorber and a control system and method therefor, a vehicle, a device, and a medium. The magnetorheological shock absorber comprises: a single-tube shock absorber, which comprises a cylinder tube and a damping piston, wherein the cylinder tube is provided with a liquid cavity for accommodating a magnetorheological fluid, and the damping piston is disposed in the liquid cavity and divides the liquid cavity into a first cavity and a second cavity that are in communication with each other; an overflow channel, one end of the overflow channel being in communication with the first cavity, and the other end of the overflow channel being in communication with the second cavity; and an electric control valve, which is disposed on the overflow channel. The control system for the magnetorheological shock absorber comprises: the magnetorheological shock absorber; a temperature sensor, which is configured to be capable of obtaining temperature data of the magnetorheological shock absorber; and a control apparatus, which is configured to control the electric control valve to open when the temperature data is lower than a set temperature. The present invention can solve the problem of high damping force of an existing magnetorheological shock absorber in a low-temperature environment and the problem of reductions in maximum damping force and adjustment ratio of the existing magnetorheological shock absorber.

Description

Magneto-rheological damper, control system and method thereof, vehicle, device and medium TECHNICAL FIELD

[0001] The present application relates to the technical field of vehicles, in particular to a magneto-rheological damper, a control system and method thereof, a vehicle, a device and a medium. BACKGROUND

[0002] The magneto-rheological damper is a semi-active single-cylinder damper. Since the magneto-rheological fluid changes the fluid state characteristics under the action of a magnetic field, the magneto-rheological damper generates a magnetic field by electric current and controls the strength of the magnetic field, thereby controlling the damping force.

[0003] The magneto-rheological fluid is mainly composed of base fluid and composite metal particles, and various additives are added to improve wear resistance, sedimentation and other problems. Due to the inherent characteristics of the magneto-rheological fluid, the magneto-rheological fluid has poor flowability in low temperature environment, resulting in high damping force of the magneto-rheological damper in low temperature environment, which cannot provide good damping effect for the vehicle.

[0004] At present, although researchers have proposed different liquid formulations to improve the low temperature performance of the magneto-rheological fluid, this method causes new problems such as decrease of maximum damping force and decrease of adjustment multiple of the magneto-rheological damper.

[0005] SUMMARY

[0006] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application proposes a magneto-rheological damper, a control system and method thereof, a vehicle, a device and a medium, which not only solves the problem of high damping force of the magneto-rheological damper in low temperature environment in the prior art, but also avoids the problems of decrease of maximum damping force and decrease of adjustment multiple.

[0007] The first aspect of the present application provides a magneto-rheological damper, comprising:

[0008] A single-cylinder damper body comprising a cylinder and a damping piston, the cylinder having a liquid cavity for containing a magneto-rheological fluid, the damping piston being arranged in the liquid cavity and dividing the liquid cavity into a first cavity and a second cavity in communication;

[0009] An overflow channel, one end of the overflow channel being in communication with the first cavity, and the other end being in communication with the second cavity;

[0010] An electrically controlled valve arranged on the overflow channel.

[0011] The magnetorheological damper according to the first aspect of the present application has at least the following advantages: the overflow passage and the electrically controlled valve are added to the single-cylinder damper body, the two ends of the overflow passage are connected with the first cavity and the second cavity of the single-cylinder damper body respectively, and the electrically controlled valve is arranged on the overflow passage. Therefore, in the normal temperature state, the electrically controlled valve is closed, and the overflow passage is in the cut-off state. Then, the magnetorheological fluid in the first cavity and the second cavity cannot flow through the electrically controlled valve and the overflow passage, but can only pass through the damping piston, so that all the damping force provided by the magnetorheological damper is generated by the movement of the damping piston. In the low temperature state, the electrically controlled valve is opened, and the overflow passage is in the on state. Then, the magnetorheological fluid in the first cavity and the second cavity can flow through the electrically controlled valve and the overflow passage, the flow of the magnetorheological fluid in the damping piston is reduced, and the damping force of the magnetorheological damper is reduced. At the same time, the flow of the magnetorheological fluid passing through the damping piston can be controlled by adjusting the opening size of the electrically controlled valve, so that the damping force of the magnetorheological damper in the low temperature environment can be effectively adjusted.

[0012] In this way, the problem that the damping force of the magnetorheological damper in the prior art is high in the low temperature environment can be overcome, and the maximum damping force and the adjustment multiple of the magnetorheological damper can be prevented from being reduced.

[0013] In some embodiments of the present application, the electrically controlled valve is an electromagnetic valve.

[0014] In some embodiments of the present application, the electrically controlled valve comprises:

[0015] a valve seat, provided with a valve cavity and a first valve port and a second valve port communicated with the valve cavity, the first valve port being communicated with the first cavity, and the second valve port being communicated with the overflow passage;

[0016] a valve core, arranged in the valve cavity;

[0017] a reset spring, one end of the reset spring being connected with the valve seat, and the other end of the reset spring being connected with the valve core, the reset spring being configured to drive the valve core to close the first valve port;

[0018] a coil winding, arranged on the valve seat and configured to magnetically attract the valve core when powered on, so that the valve core is away from the first valve port and opens the first valve port.

[0019] In some embodiments of the present application, the valve seat comprises a shell, an end cover and a fixing seat; the shell and the end cover are connected and jointly enclose the valve cavity, the end cover is provided with the first valve port, the fixing seat is arranged in the valve cavity and fixedly connected with the shell, the coil winding is arranged on the fixing seat, and one end of the reset spring is connected with the fixing seat.

[0020] In some embodiments of the present application, the fixed seat is provided with a guide groove on one side of the valve core, the valve core is provided with a guide part on one side of the fixed seat, the guide part is provided with a limiting groove, the outer circumferential surface of the guide part is in contact with the inner circumferential surface of the guide groove, one end of the reset spring abuts against the groove bottom of the guide groove, and the other end abuts against the groove bottom of the limiting groove.

[0021] The second aspect of the present application provides a control system of a magneto-rheological damper, comprising:

[0022] The magneto-rheological damper according to the first aspect of the present application;

[0023] A temperature sensor configured to obtain temperature data of the magneto-rheological damper;

[0024] A control device electrically connected with the temperature sensor and the magneto-rheological damper respectively, and configured to control the electrically controlled valve to open according to the temperature data being lower than a set temperature.

[0025] The control system of the magneto-rheological damper according to the second aspect of the present application has at least the following beneficial effects: the temperature data of the magneto-rheological damper is collected by the temperature sensor, so that the control device compares the obtained temperature data with the set temperature, and if the temperature data is less than the set temperature, it is judged that the magneto-rheological damper is in a low-temperature state, at this time, the poor flowability of the magneto-rheological fluid is easy to cause the damping force of the magneto-rheological damper to be high, then the control device sends an opening instruction to the electrically controlled valve to make the overflow channel be in a conductive state, and in the process of the movement of the damping piston, part of the magneto-rheological fluid flows through the overflow channel, thereby reducing the flow of the magneto-rheological fluid through the damping piston and reducing the damping force of the magneto-rheological damper.

[0026] In some embodiments of the present application, the control device comprises a vehicle controller and a chassis domain controller, the vehicle controller is configured to obtain driving state data of the vehicle and send it to the chassis domain controller, and the chassis domain controller is configured to obtain current data of the damping piston and control the opening degree of the electrically controlled valve according to the driving state data, the temperature data and the current data.

[0027] In some embodiments of the present application, the chassis domain controller is configured to control the opening degree of the electrically controlled valve to be smaller according to the current data being larger when the temperature data is lower than the set temperature and the vehicle is in a driving state.

[0028] The third aspect of the present application provides a control method of a magneto-rheological damper, applied to the magneto-rheological damper according to the first aspect of the present application, comprising the following steps:

[0029] acquiring temperature data of the magneto-rheological damper when the vehicle is in a driving state;

[0030] determining whether the temperature data is lower than a set temperature;

[0031] if yes, controlling the electric control valve to open;

[0032] if no, controlling the electric control valve to close.

[0033] The control method of the magneto-rheological damper according to the third aspect of the present application has at least the following beneficial effects: in the driving process of the vehicle, by comparing the acquired temperature data of the magneto-rheological damper with the set temperature, it is determined whether the magneto-rheological damper is in a low-temperature state and the electric control valve needs to be opened; when the temperature of the magneto-rheological damper is greater than or equal to the set temperature, the flowability of the magneto-rheological fluid is good, and the electric control valve does not need to be opened; when the temperature of the magneto-rheological damper is less than the set temperature, the flowability of the magneto-rheological fluid is poor, resulting in high damping force of the magneto-rheological damper; at this time, by opening the electric control valve, the magneto-rheological fluid in the first cavity and the second cavity can flow along the overflow channel, the flow of the magneto-rheological fluid passing through the damping piston is reduced, and the damping force of the magneto-rheological damper is further reduced.

[0034] In some embodiments of the present application, the if yes, controlling the electric control valve to open, comprises the following steps:

[0035] if yes, acquiring current data of the damping piston;

[0036] controlling the opening degree of the electric control valve according to the current-opening degree curve; wherein on the current-opening degree curve, the greater the current data is, the smaller the opening degree of the electric control valve is.

[0037] In some embodiments of the present application, the controlling the opening degree of the electric control valve according to the current-opening degree curve comprises the following steps:

[0038] acquiring driving duration of the vehicle when the temperature data is in the i-th temperature interval; wherein the temperature intervals are provided with n, the temperature of the m-th temperature interval is higher than the temperature of the (m+1)-th temperature interval, m, n and i are natural numbers, and n>1, 1

[0039] determining whether the driving duration reaches a first set duration;

[0040] if yes, controlling the opening degree of the electric control valve according to the current-opening degree curve of the (i-1)-th temperature interval.

[0041] In some embodiments of the present application, the controlling the opening degree of the electric control valve according to the current-opening degree curve further comprises the following steps:

[0042] acquire a driving duration of the vehicle when the temperature data is in the first temperature interval;

[0043] determine whether the driving duration reaches a second set duration;

[0044] if yes, control the electric control valve to be closed.

[0045] The fourth aspect of the present application provides a vehicle comprising the magneto-rheological damper according to the first aspect of the present application, or comprising the control system of the magneto-rheological damper according to the second aspect of the present application.

[0046] The vehicle according to the fourth aspect of the present application has at least the following beneficial effects: the magneto-rheological damper or the control system of the magneto-rheological damper is installed on the vehicle, when the vehicle is in a driving state, if the temperature of the magneto-rheological damper is too low to cause the flowability of the magneto-rheological fluid to be poor, the flow of the magneto-rheological fluid in the damping piston is reduced by opening the electric control valve, so as to reduce the damping force, and the maximum damping force and the adjustment multiple of the magneto-rheological damper are avoided to be reduced.

[0047] The fifth aspect of the present application provides an electronic device comprising:

[0048] at least one processor; and,

[0049] a memory connected with the at least one processor in communication; wherein the memory stores a computer program executable by the at least one processor, and the computer program is executed by the at least one processor to enable the at least one processor to execute the control method of the magneto-rheological damper according to the third aspect of the present application.

[0050] The sixth aspect of the present application provides a computer readable storage medium, which stores a computer program executable by a processor, and the computer program is executed by the processor to implement the control method of the magneto-rheological damper according to the third aspect of the present application.

[0051] Other features and advantages of the present application will be set forth in the following description, and in part will become apparent from the description, or can be learned by practice of the present application. The objects and other advantages of the present application will be realized and achieved by means of the structures particularly pointed out in the description and the appended claims. BRIEF DESCRIPTION OF DRAWINGS

[0052] Fig. 1 is a schematic diagram of a perspective structure of a magneto-rheological damper according to an embodiment of the present application;

[0053] Fig. 2 is a schematic diagram of an internal structure of a magneto-rheological damper according to an embodiment of the present application;

[0054] Fig. 3 is an enlarged schematic view of part A in Fig. 2;

[0055] Fig. 4 is a flowchart of a control method of a magneto-rheological damper according to an embodiment of the present application;

[0056] Fig. 5 is a flowchart of step S3 in the control method of the magneto-rheological damper according to an embodiment of the present application;

[0057] Fig. 6 is a flowchart of step S32 in the control method of the magneto-rheological damper according to an embodiment of the present application;

[0058] Fig. 7 is a flowchart of step S32 in the control method of the magneto-rheological damper according to another embodiment of the present application;

[0059] Fig. 8 is a specific control flowchart of step S32 in the control method of the magneto-rheological damper according to an embodiment of the present application;

[0060] Fig. 9 is a schematic view of a current-opening curve according to an embodiment of the present application;

[0061] Fig. 10 is a schematic view of a structure of an electronic device according to an embodiment of the present application.

[0062] Reference signs: 100, single-tube damper main body; 110, piston rod; 120, cylinder tube; 121, first cavity; 122, second cavity; 123, gas cavity; 124, first connecting port; 125, second connecting port; 130, damping piston; 140, floating piston; 150, sealing member; 200, electrically-controlled valve; 211, housing; 212, fixed seat; 213, end cover; 214, valve cavity; 215, first valve port; 216, second valve port; 217, guide groove; 220, valve core; 221, limiting groove; 230, return spring; 240, coil winding; 250, support ring; 260, sealing ring; 300, overflow passage. DETAILED DESCRIPTION

[0063] Embodiments of the present application are described in detail below with reference to the attached drawings, which show by way of example, embodiments in which like numerals indicate like elements throughout the several figures. The embodiments described below are merely exemplary for the purposes of explanation and are not to be construed as limiting the present application.

[0064] In the description of the present application, it is to be understood that the features defined with "first", "second" can include one or more of the features explicitly or implicitly. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0065] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "connected", "connected" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium, and it can be connected inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0066] The magneto-rheological shock absorber is a semi-active single-cylinder shock absorber. The magneto-rheological shock absorber has the characteristics of high adjustable damping force, easy computer variable damping real-time control, compact structure, and small external input energy, and is increasingly valued in the automotive field.

[0067] The magneto-rheological shock absorber has no valve plate in the damping piston inside, but is installed with two groups of coils. When the coils are energized, a magnetic field is generated. At the same time, a magneto-rheological fluid is used instead of the shock absorber oil. Since the magneto-rheological fluid changes the fluid state characteristics under the action of the magnetic field, the magneto-rheological shock absorber generates a magnetic field through the current-carrying coil, and controls the size of the generated damping force by controlling the strength of the magnetic field.

[0068] The magneto-rheological fluid is mainly composed of base fluid and composite metal particles, and various additives are added to improve wear resistance, sedimentation and other problems. However, due to the inherent characteristics of the magneto-rheological fluid, the flowability of the magneto-rheological fluid is poor in low temperature environment, that is, the low temperature performance of the magneto-rheological fluid is poor, so that the damping force of the magneto-rheological shock absorber is increased in low temperature environment, and the magneto-rheological shock absorber cannot provide good damping effect for the vehicle.

[0069] The existing magneto-rheological shock absorber is taken as an example for description.

[0070] In normal temperature environment and low temperature environment such as-30℃, the damping force of the magneto-rheological shock absorber is tested by setting the coil current of the magneto-rheological shock absorber to 0A and 3A respectively, and the corresponding test data is collected. Through many times of damping force test, a plurality of groups of data of the damping force of the magneto-rheological shock absorber in low temperature environment such as-30℃ and in normal temperature environment are obtained.

[0071] The relationship between the damping force of the magneto-rheological shock absorber in low temperature environment and the damping force in normal temperature environment is as follows:

[0072] The change rate of-30℃=(-30℃ damping force-normal temperature environment damping force) / normal temperature environment damping force.

[0073] Table 1 is as follows:

[0074] As shown in Table 1, the damping force of the magneto-rheological damper is increased by more than 4 times relative to the normal temperature when the temperature is-30 DEG C and the coil current is 0 A, and the damping force of the magneto-rheological damper is increased by a smaller amplitude relative to the normal temperature when the temperature is-30 DEG C and the coil current is 3 A.

[0075] At present, although researchers have proposed a technical solution for improving the low-temperature performance of the magneto-rheological fluid by studying different liquid formulations, this solution can cause new problems such as a decrease in the maximum damping force of the magneto-rheological damper and a decrease in the adjustment multiple, thereby causing the magneto-rheological damper to be unable to provide an excellent damping effect for the vehicle.

[0076] Based on the above technical problems, the embodiments of the present application provide a magneto-rheological damper, a control system and method thereof, a vehicle, equipment and a medium, which not only can solve the problem of an increase in the damping force of the magneto-rheological damper in a low-temperature environment, but also can effectively avoid the problems of a decrease in the maximum damping force of the magneto-rheological damper and a decrease in the adjustment multiple.

[0077] The magneto-rheological damper, the control system and method thereof, the vehicle, the equipment and the medium provided by the embodiments of the present application are described below with reference to FIGS. 1 to 10.

[0078] As shown in FIGS. 1 to 3, the magneto-rheological damper according to the first aspect of the embodiments of the present application can be used as an automobile part on a vehicle to provide an excellent damping effect for the vehicle.

[0079] The structure of the magneto-rheological damper includes a single-cylinder damper body 100, an overflow channel 300 and an electrically controlled valve 200.

[0080] The single-cylinder damper body 100 includes a cylinder 120 and a damping piston 130.

[0081] The cylinder 120 is hollow inside to form a liquid cavity, which can be in a cylindrical shape and is used to contain the magneto-rheological fluid. The damping piston 130 is arranged in the liquid cavity of the cylinder 120, the outer circumferential surface of the damping piston 130 is in contact with the inner circumferential surface of the liquid cavity, so that the damping piston 130 is in sliding fit with the cylinder 120, and the damping piston 130 divides the liquid cavity into a first cavity 121 and a second cavity 122. Since the damping piston 130 is provided with a damping channel, the damping channel extends through the damping piston 130 in the axial direction, the damping channel is provided in multiple groups and is uniformly arranged along the circumferential direction of the damping piston 130, so that the first cavity 121 and the second cavity 122 are connected, and the magneto-rheological fluid can flow back and forth between the first cavity 121 and the second cavity 122 when the damping piston 130 moves back and forth.

[0082] The outer circumferential surface of the damping piston 130 is provided with a plurality of grooves which are spaced along the axial direction of the damping piston 130, and a coil is arranged in each groove. When the coil is energized, a magnetic field is generated at the damping piston 130, thereby changing the rheological properties of the MR fluid and adjusting the damping force provided by the MR damper.

[0083] In addition, the single-tube damper body 100 further comprises a piston rod 110 and a floating piston 140.

[0084] One end of the cylinder barrel 120 is provided with a guide hole, and one end of the piston rod 110 extends into the guide hole and is fixedly connected with the damping piston 130. The other end of the piston rod 110 is located outside the liquid chamber and can be connected with the vehicle body. The end of the cylinder barrel 120 close to the guide hole is provided with a sealing member 150 to oil seal the piston rod 110 and prevent the MR fluid from leaking from the gap between the piston rod 110 and the cylinder barrel 120. The wiring part of the coil can be designed to pass through the through hole in the piston rod 110.

[0085] The cylinder barrel 120 is further provided with a gas chamber 123, and the floating piston 140 is arranged in the cylinder barrel 120 and located between the liquid chamber and the gas chamber 123 to separate the liquid chamber and the gas chamber 123 and prevent gas-liquid mixing. The floating piston 140 is located on the side of the damping piston 130 away from the piston rod 110. The gas chamber 123 is filled with an inert gas such as nitrogen.

[0086] It can be understood that the outer circumferential surface of the damping piston 130 and the outer circumferential surface of the floating piston 140 are provided with sealing rings 260 which are in contact with the inner circumferential surface of the liquid chamber or the inner circumferential surface of the gas chamber 123. The single-tube damper body 100 is a prior structure, and those skilled in the art should understand its specific structure and working principle.

[0087] One end of the overflow passage 300 is in communication with the first chamber 121, and the other end of the overflow passage 300 is in communication with the second chamber 122. The electrically controlled valve 200 is arranged on the overflow passage 300, and the electrically controlled valve 200 is used to control the state of the overflow passage 300 and switch the overflow passage 300 between the cut-off state and the conduction state. The electrically controlled valve 200 is an electromagnetic valve.

[0088] Specifically, the cylinder 120 is provided with a first connecting port 124 and a second connecting port 125. The first connecting port 124 is in communication with the first cavity 121, and the second connecting port 125 is in communication with the second cavity 122. The overflow passage 300 can be composed of a metal pipe. One end of the overflow passage 300 is connected to the first connecting port 124, and the other end of the overflow passage 300 is connected to the second connecting port 125. Therefore, the magnetorheological fluid in the first cavity 121 can flow into the overflow passage 300 through the first connecting port 124 and flow to the second cavity 122, and the magnetorheological fluid in the second cavity 122 can flow into the overflow passage 300 through the second connecting port 125 and flow to the first cavity 121.

[0089] It can be understood that the magnetorheological fluid is filled in the first cavity 121, the second cavity 122 and the overflow passage 300. In the case that the overflow passage 300 is in the cut-off state, when the damping piston 130 moves axially relative to the cylinder 120, the magnetorheological fluid cannot flow along the overflow passage 300, but only flows along the damping passage of the damping piston 130. In the case that the overflow passage 300 is in the on state, when the damping piston 130 moves axially along the cylinder 120, the magnetorheological fluid can not only flow from the damping passage of the damping piston 130, but also flow along the overflow passage 300.

[0090] The first connecting port 124 can be arranged on the side of the first cavity 121 away from the damping piston 130, and the second connecting port 125 can be arranged on the side of the second cavity 122 away from the damping piston 130. Then, in the case that the overflow passage 300 is in the on state, when the damping piston 130 moves within its set movement range, the magnetorheological fluid can flow into the overflow passage 300.

[0091] In the present embodiment, the first connecting port 124 and the second connecting port 125 are both located on the same side of the cylinder 120 in the circumferential direction. The first cavity 121 is located on the side of the damping piston 130 away from the piston rod 110, and the second cavity 122 is located on the side of the damping piston 130 close to the piston rod 110. The piston rod 110 is located above the damping piston 130, and the floating piston 140 is located below the damping piston 130. Therefore, the second cavity 122 is located above the first cavity 121, and the gas cavity 123 is located below the first cavity 121.

[0092] So, in the case that the electric control valve 200 is in the open state, when the damping piston 130 moves downward, the magnetorheological fluid in the first cavity 121 can flow to the second cavity 122 through the damping passage of the damping piston 130, and the magnetorheological fluid in the first cavity 121 can flow into the second cavity 122 through the electric control valve 200 and the overflow passage 300; when the damping piston 130 moves upward, the magnetorheological fluid in the second cavity 122 can flow to the first cavity 121 through the damping passage of the damping piston 130, and the magnetorheological fluid in the second cavity 122 can flow into the first cavity 121 through the electric control valve 200 and the overflow passage 300.

[0093] It can be understood that the overflow passage 300 can be designed separately from the cylinder 120, or can be integrally arranged with the cylinder 120. In the embodiment, the overflow passage 300 is located outside the cylinder 120, and the overflow passage 300 can be detachably connected with the electric control valve 200 and the cylinder 120, respectively.

[0094] In the magnetorheological damper provided by the embodiment of the present application, since the overflow passage 300 and the electric control valve 200 are added on the basis of the single-cylinder damper body 100, the two ends of the overflow passage 300 are connected with the first cavity 121 and the second cavity 122 of the single-cylinder damper body 100, respectively, and the electric control valve 200 is arranged on the overflow passage 300, therefore, in the normal temperature state, the electric control valve 200 is closed, and the overflow passage 300 is in the cut-off state, then the magnetorheological fluid in the first cavity 121 and the second cavity 122 cannot flow through the electric control valve 200 and the overflow passage 300, but only can flow through the damping piston 130, so that all the damping force provided by the magnetorheological damper is generated by the movement of the damping piston 130; in the low-temperature state, the electric control valve 200 is opened, and the overflow passage 300 is in the conduction state, then the magnetorheological fluid in the first cavity 121 and the second cavity 122 can flow through the electric control valve 200 and the overflow passage 300, so as to reduce the flow of the magnetorheological fluid in the damping piston 130, thereby reducing the damping force of the magnetorheological damper. Meanwhile, the flow of the magnetorheological fluid flowing through the damping piston 130 can be controlled by adjusting the opening degree of the electric control valve 200, so as to effectively adjust the damping force of the magnetorheological damper in the low-temperature environment.

[0095] The present application adopts such a structure design, in the low-temperature state, the opening and closing degree of the electric control valve 200 is controlled, so as to increase the flow of the magnetorheological fluid in the overflow passage 300, thereby achieving the purpose of reducing the damping force, therefore, the present application can overcome the problem that the damping force of the magnetorheological damper in the prior art is high in the low-temperature environment, and effectively prevent the problems of the reduction of the maximum damping force and the adjustment multiple of the magnetorheological damper.

[0096] In some embodiments, the structure of the electrically controlled valve 200 includes a valve seat, a valve core 220, a reset spring 230 and a coil winding 240.

[0097] The valve seat is provided with a valve cavity 214, and the valve seat is further provided with a first valve port 215 and a second valve port 216, both of which are communicated with the valve cavity 214. After the valve seat is connected with the cylinder barrel 120 and the overflow passage 300 respectively, the first valve port 215 is communicated with the first cavity 121, and the second valve port 216 is communicated with one end of the overflow passage 300, and the other end of the overflow passage 300 is communicated with the second cavity 122.

[0098] In the present embodiment, the valve seat is arranged outside the cylinder barrel 120 and fixedly connected with the cylinder barrel 120, and the valve seat is located below the damping piston 130. The first valve port 215 is open towards the outer wall of the cylinder barrel 120 and connected with the first connecting port 124, and the second valve port 216 is open upwards and connected with one end of the overflow passage 300, and the other end of the overflow passage 300 is connected with the second connecting port 125. Therefore, the magnetorheological fluid can flow into the valve cavity 214 through the first valve port 215 or the second valve port 216.

[0099] The valve core 220 is arranged in the valve cavity 214, and the valve core 220 is used to block or unblock the first valve port 215. When the valve core 220 is close to and blocks the first valve port 215, the electrically controlled valve 200 is in a closed state, so that the magnetorheological fluid in the first cavity 121 and the second cavity 122 cannot flow through the overflow passage 300 and the valve cavity 214. When the valve core 220 is away from and opens the first valve port 215, the electrically controlled valve 200 is in an open state, so that the magnetorheological fluid in the first cavity 121 and the second cavity 122 can flow through the overflow passage 300 and the valve cavity 214.

[0100] One end of the reset spring 230 is connected with the valve seat, and the other end of the reset spring 230 is connected with the valve core 220. The reset spring 230 is configured to drive the valve core 220 to be close to and block the first valve port 215. The reset spring 230 provides support force for the valve core 220, and the elastic force of the reset spring 230 provides driving action for the movement of the valve core 220.

[0101] The coil winding 240 is arranged on the valve seat, and the coil winding 240 is configured to generate magnetic attraction to the valve core 220 when energized, so as to drive the valve core 220 to be away from and open the first valve port 215. The coil winding 240 generates a magnetic field after being powered on, and the magnetic field disappears after being powered off. The valve core 220 can be made of a magnetic conductive material such as iron, or can be a magnet.

[0102] It can be understood that, in the case of coil winding 240 power loss, the valve core 220 will be affected by the elastic force of the reset spring 230 to move close to the first valve port 215, and block the first valve port 215, prompting the electric control valve 200 to be in the closed state. In the case of coil winding 240 power, the valve core 220 will be affected by the magnetic force and the elastic force of the reset spring 230, and since the magnetic force is stronger than the elastic force of the reset spring 230, the valve core 220 will overcome the elastic force and move away from the first valve port 215, and open the first valve port 215. Because the magneto-rheological shock absorber works in low temperature state for a short time, through such design, the electric energy can be saved.

[0103] Further, the structure of the valve seat includes a housing 211, an end cover 213 and a fixed seat 212.

[0104] The housing 211 is provided with an opening structure at both ends in the horizontal direction, the housing 211 and the end cover 213 are fixedly connected, and the end cover 213 is arranged at one of the opening structures of the housing 211. The fixed seat 212 is arranged in the valve cavity 214 and located at the other opening structure of the housing 211, and the fixed seat 212 is fixedly connected with the housing 211. The fixed seat 212 and the end cover 213 are arranged opposite in the horizontal direction. Moreover, the fixed seat 212, the end cover 213 and the housing 211 together form a valve cavity 214. The end cover 213 is provided with a first valve port 215, and the opening direction of the first valve port 215 is perpendicular to the up-down direction.

[0105] The coil winding 240 is arranged on the fixed seat 212, and the fixed seat 212 provides a mounting and supporting position for the coil winding 240. Specifically, the outer circumferential surface of the fixed seat 212 is provided with a receiving groove, and the coil winding 240 is arranged in the receiving groove. Moreover, the power connection part of the coil winding 240 is arranged through the wire hole of the fixed seat 212, extends out of the valve cavity 214, and is electrically connected with the power supply. The valve core 220 is located between the end cover 213 and the fixed seat 212, one end of the reset spring 230 is connected with the fixed seat 212, and the other end of the reset spring 230 is connected with the valve core 220.

[0106] In the embodiment, the shell 211 is fixedly connected with the cylinder barrel 120, the end cover 213 extends towards the direction close to the valve core 220 and forms a convex part, the first valve port 215 extends through the horizontal direction of the convex part, and the outer circumferential surface of the end cover 213 is in contact with the inner circumferential surface of the shell 211. In addition, the electric control valve 200 further comprises a sealing ring 260 and a support ring 250. The support ring 250 is arranged in the valve cavity 214, the outer circumferential surface of the support ring 250 is connected with the inner circumferential surface of the shell 211, the convex part of the end cover 213 penetrates the center hole of the support ring 250, and the support ring 250 can provide a supporting action on the convex part. Moreover, at least one sealing ring 260 is arranged between the convex part and the support ring 250 to prevent the magnetic rheological fluid from flowing back through the gap between the support ring 250 and the convex part. At least one sealing ring 260 is also arranged between the fixed seat 212 and the shell 211 to prevent the magnetic rheological fluid from leaking through the gap between the fixed seat 212 and the shell 211.

[0107] The valve core 220 is oppositely arranged with the first valve port 215 of the convex part in the horizontal direction, the surface close to the convex part of the valve core 220 is a plane, the valve core 220 abuts against the convex part, so that the valve core 220 can block the first valve port 215. The first valve port 215 can be a tapered port, and the first valve port 215 gradually decreases from the first cavity 121 to the valve cavity 214.

[0108] Further, the fixed seat 212 is provided with a guide groove 217 on the side close to the valve core 220, and the opening of the guide groove 217 is open to the direction of the valve core 220. The valve core 220 is provided with a guide part on the side close to the fixed seat 212, the guide part is integrally formed with the valve core 220, the guide part is provided with a limiting groove 221, and the opening of the limiting groove 221 is open to the direction of the fixed seat 212. After the guide part is inserted into the guide groove 217, the outer circumferential surface of the guide part is in contact with the inner circumferential surface of the guide groove 217, the guide groove 217 and the guide part are matched to provide a guide action for the movement of the valve core 220, so that the valve core 220 can move stably in the horizontal direction and exert a blocking action on the first valve port 215.

[0109] The reset spring 230 is arranged between the limiting groove 221 of the valve core 220 and the guide groove 217 of the fixed seat 212, one end of the reset spring 230 abuts against the groove bottom of the guide groove 217, and the other end of the reset spring 230 abuts against the groove bottom of the limiting groove 221. In this way, the reset spring 230 does not need to be fixedly connected with the fixed seat 212 and the valve core 220 respectively, so that the assembly difficulty of the electric control valve 200 is reduced.

[0110] In the embodiment, the guide groove 217 and the limiting groove 221 are both in a cylindrical shape, and the cross section of the guide part is circular.

[0111] In the normal temperature state, the valve core 220 can abut against the convex portion and block the first valve port 215 by the elastic force of the reset spring 230, so that the overflow passage 300 is in the state of being cut off and closed. Then, the magnetorheological fluid can only pass through the damping passage of the damping piston 130, and the damping force of the magnetorheological damper is generated by the damping piston 130.

[0112] In the low temperature state, the coil winding 240 of the electric control valve 200 is energized to generate a magnetic field, so that the valve core 220 is subjected to magnetic attraction and moves towards the fixed seat 212, thereby opening the first valve port 215, so that the overflow passage 300 is in the state of being turned on and opened. Then, the magnetorheological fluid can pass through the electric control valve 200 and the overflow passage 300 to flow in the first cavity 121 and the second cavity 122, thereby reducing the flow of the magnetorheological fluid in the damping passage of the damping piston 130 and reducing the damping force of the magnetorheological damper.

[0113] It can be understood that the total flow of the magnetorheological fluid is the sum of the flow of the magnetorheological fluid flowing through the overflow passage 300 and the flow of the magnetorheological fluid flowing through the damping piston 130. When the design parameters of the magnetorheological damper are set, the opening degree of the electric control valve 200 will affect the flow ratio of the magnetorheological fluid flowing through the overflow passage 300 and the damping piston 130. The greater the opening degree of the electric control valve 200, the less the flow of the magnetorheological fluid flowing through the damping piston 130, the greater the flow of the magnetorheological fluid flowing through the overflow passage 300, and the smaller the generated damping force. Conversely, the greater the generated damping force.

[0114] The control system of the magnetorheological damper according to the second aspect of the present application comprises a temperature sensor, a control device and the magnetorheological damper of the first aspect of the present application.

[0115] The temperature sensor is configured to obtain temperature data of the magnetorheological damper. The control device is configured to control the electric control valve 200 to open according to the temperature data being lower than a set temperature.

[0116] It can be understood that the temperature sensor can directly measure the temperature of the cylinder barrel 120, or can be arranged inside the piston rod 110 to measure the temperature of the piston rod 110 or the magnetorheological fluid. The control device can be a PLC controller, a 51 single-chip microcomputer, etc., or can be an existing control system on the vehicle, such as a vehicle controller and a chassis domain controller. The set temperature can be set according to the actual situation, and can be set to 0℃, which is not limited specifically herein.

[0117] The temperature sensor transmits the temperature data to the control device after collecting the temperature data of the MR damper, and the control device compares the temperature data with the set temperature; if the temperature data is less than the set temperature, it is judged that the MR damper is in a low-temperature state, at this time, the poor flowability of the MR fluid can easily cause the damping force of the MR damper to be high, so the control device sends an opening instruction to the electric control valve 200; after the electric control valve 200 is opened, the overflow channel 300 is in a conductive state, so part of the MR fluid flows through the overflow channel 300 during the movement of the damping piston 130, reducing the flow of the MR fluid through the damping piston 130, thereby reducing the damping force of the MR damper.

[0118] If the temperature data is greater than or equal to the set temperature, it is judged that the MR damper is in a normal temperature state, at this time, the flowability of the MR fluid is good, and the electric control valve 200 does not need to be opened, so the overflow channel 300 is in a cut-off state, and the MR fluid passes through the damping piston 130, so that the damping force of the MR damper is generated by the damping piston 130. It can be understood that the normal temperature state is relative to the low-temperature state, and is not specifically 25℃.

[0119] In some embodiments, the control device includes a vehicle controller and a chassis domain controller.

[0120] The vehicle controller and the chassis domain controller are electrically connected, and the temperature sensor and the MR damper are respectively electrically connected to the chassis domain controller. The vehicle controller is configured to obtain the driving state data of the vehicle and send it to the chassis domain controller. The chassis domain controller is configured to obtain the current data of the damping piston 130 and control the opening degree of the electric control valve 200 according to the driving state data, the temperature data and the current data.

[0121] It can be understood that in order to obtain the driving state data of the vehicle, the wheel speed of the vehicle can be monitored, specifically, the vehicle controller can obtain the vehicle speed data through the wheel speed sensor, if the vehicle speed data is not zero, it indicates that the vehicle is in a driving state, and the MR damper needs to provide good damping effect; if the vehicle speed data is zero, it indicates that the vehicle is in a stopped state, and the MR damper does not need to work.

[0122] Since the MR damper belongs to a semi-active damper type with adjustable damping, and the MR fluid belongs to a new type of fluid with controllable flowability, it presents the characteristics of a low-viscosity Newtonian fluid when there is no external magnetic field. When an external magnetic field is applied, it presents the characteristics of a high-viscosity, low-flow Bingham fluid, so the chassis domain controller can control the on-off and current of the coil on the damping piston 130 to provide good damping effect for the vehicle. The greater the current flowing through the coil, the greater the flowability of the MR fluid, and the more MR fluid flows through the damping piston 130.

[0123] Therefore, the opening degree of the electric control valve 200 needs to be adjusted according to the driving state data of the vehicle, the temperature data of the MR damper and the current data of the damping piston 130, so as to control the flow of the MR fluid flowing through the overflow passage 300.

[0124] Specifically, the chassis domain controller is configured to control the opening degree of the electric control valve 200 to be smaller when the temperature data is lower than the set temperature and the vehicle is in the driving state.

[0125] In the case that the vehicle is in the driving state and the MR damper is in the low-temperature state, the coil on the damping piston 130 is energized by the chassis domain controller, and the current of the coil is adjusted to change the rheological properties of the MR fluid to meet the comfort and handling requirements of the vehicle. However, since the flowability of the MR fluid is poor at low temperature, the electric control valve 200 and the overflow passage 300 can make up for this shortcoming. However, if the opening degree of the electric control valve 200 is too large or too small, it cannot bring good damping effect, so the opening degree of the electric control valve 200 needs to be controlled according to the current data of the damping piston 130. If the current data is large, the opening degree of the electric control valve 200 needs to be small to reduce the flow of the MR fluid through the overflow passage 300 to avoid too small damping force; if the current data is small, the opening degree of the electric control valve 200 needs to be large to increase the flow of the MR fluid through the overflow passage 300 to avoid too high damping force.

[0126] As shown in FIG. 4, the control method of the MR damper according to the third aspect of the present application is applied to the MR damper of the first aspect of the present application, and the control method of the MR damper comprises the following steps:

[0127] Step S1: When the vehicle is in the driving state, the temperature data of the MR damper is obtained.

[0128] Step S2: Determine whether the temperature data is lower than the set temperature.

[0129] Step S3: If yes, control the electric control valve 200 to open.

[0130] Step S4: If no, control the electric control valve 200 to close.

[0131] It can be understood that in step S1, if the vehicle is not in the driving state, the vehicle has no need for damping, then the MR damper can be in a stopped or standby state, at this time, the temperature sensor does not need to collect the temperature data of the MR damper. If it is determined through the collected vehicle speed data that the current vehicle is in the driving state, the temperature sensor will work to obtain the temperature data of the MR damper to determine the flowability of the MR fluid.

[0132] In step S2, after the chassis domain controller acquires the temperature data, it starts to compare the temperature data with the set temperature. If the temperature data is greater than or equal to the set temperature, it proves that the flowability of the MR fluid is good, and step S4 is executed. If the temperature data is less than the set temperature, it proves that the flowability of the MR fluid is poor, and step S3 is executed.

[0133] With the above control method, in the process of vehicle driving, by comparing the acquired temperature data of the MR damper with the set temperature, it is determined whether the MR damper is in a low-temperature state and the electrically-controlled valve 200 needs to be opened. When the temperature of the MR damper is greater than or equal to the set temperature, the flowability of the MR fluid is good, and the electrically-controlled valve 200 does not need to be opened. When the temperature of the MR damper is less than the set temperature, the flowability of the MR fluid is poor, resulting in high damping force of the MR damper. At this time, by opening the electrically-controlled valve 200, the MR fluid in the first cavity 121 and the second cavity 122 can flow along the overflow passage 300, the flow rate of the MR fluid passing through the damping piston 130 is reduced, and the damping force of the MR damper is reduced.

[0134] As shown in FIG. 5, in some embodiments, step S3, i.e., the step of opening the electrically-controlled valve 200, specifically includes the following steps:

[0135] Step S31: If yes, acquire the current data of the damping piston 130.

[0136] Step S32: According to the current-opening curve, control the opening of the electrically-controlled valve 200; wherein on the current-opening curve, the greater the current data, the smaller the opening of the electrically-controlled valve 200.

[0137] Since the opening of the electrically-controlled valve 200 affects the flow rate ratio of the MR fluid passing through the damping piston 130 and the overflow passage 300, thereby affecting the damping force, specifically, the greater the opening of the electrically-controlled valve 200, the less the flow rate of the MR fluid passing through the damping piston 130, and the smaller the damping force generated. Moreover, the current size in the damping piston 130 affects the rheological properties of the MR fluid, thereby affecting the damping force. Therefore, the opening of the electrically-controlled valve 200 needs to be adjusted according to the current size of the damping piston 130, so as to provide better damping effect for the vehicle in the low-temperature state.

[0138] The current-opening curve can be obtained according to the actual test data. As shown in FIG. 9, in the bypass valve opening-main electromagnetic valve current curve, the horizontal axis of the main electromagnetic valve current represents the current in the damping piston 130, and the vertical axis of the electric bypass opening represents the opening of the electrically-controlled valve 200.

[0139] As shown in FIG. 9, in the present embodiment, the test and data collection are respectively performed for four low temperature intervals (including low temperature a, low temperature b, low temperature c and low temperature d), and four current-opening curves are obtained according to the current data of the damping piston 130 and the opening data of the electrically controlled valve 200.

[0140] The chassis domain controller can determine the current temperature of the magneto-rheological damper in which low temperature interval according to the temperature data of the magneto-rheological damper, and determine the corresponding current-opening curve accordingly. Then, the opening of the electrically controlled valve 200 is controlled according to the current data of the damping piston 130 and the determined current-opening curve.

[0141] For example, as shown in FIG. 9, if it is determined that the current temperature of the magneto-rheological damper is in the low temperature b interval, and the current of the damping piston 130 is 0 A, the opening of the electrically controlled valve 200 is adjusted to 1 / 2; in this case, if the current of the damping piston 130 increases to 3 A, the opening of the electrically controlled valve 200 is adjusted to 0, i.e. the electrically controlled valve 200 is closed. When the opening of the electrically controlled valve 200 reaches 1, it means that the electrically controlled valve 200 is in the fully open state. For the current interval of the damping piston 130 from 0 A to 3 A, the opening of the electrically controlled valve 200 can be adjusted according to the current-opening curve corresponding to the low temperature b interval.

[0142] As shown in FIG. 9, when the current of the damping piston 130 is controlled in the current interval from 2 A to 3 A, the flowability of the magneto-rheological fluid is good, and the damping force can be reduced without passing through the overflow channel 300, so the electrically controlled valve 200 does not need to be opened, and the electrically controlled valve 200 is in the closed state. For example, for the low temperature a interval, if the current of the damping piston 130 is adjusted in the current interval from 2 A to 3 A, the opening of the electrically controlled valve 200 is kept at zero.

[0143] As shown in FIG. 6, further, the step S32, i.e. the step of controlling the opening of the electrically controlled valve 200 according to the current-opening curve, specifically includes the following steps:

[0144] Step S321: obtaining the driving duration of the vehicle when the temperature data is in the i th temperature interval; wherein the temperature interval is provided with n, the temperature of the m th temperature interval is higher than the temperature of the (m+1) th temperature interval, m, n and i are natural numbers, and n>1, 1

[0145] Step S322: determining whether the driving duration reaches the first set duration.

[0146] Step S323: if yes, controlling the opening of the electrically controlled valve 200 according to the current-opening curve of the (i-1) th temperature interval.

[0147] It can be understood that the specific value of n and the specific value of the first set duration can be set according to actual conditions, which are not limited here. From the first temperature interval to the n th temperature interval, the value of the temperature interval decreases in turn.

[0148] Since the magnetorheological shock absorber moves continuously during vehicle driving, heat is generated, causing the temperature of the magnetorheological shock absorber to continuously increase. Therefore, the current-opening curve needs to be determined according to the driving duration of the vehicle, and the opening of the electric control valve 200 is adjusted accordingly.

[0149] In this embodiment, as shown in FIG. 8, when the temperature T of the magnetorheological shock absorber is greater than or equal to 0℃, it is defined that the magnetorheological shock absorber is in a normal temperature state. At this time, the flowability of the magnetorheological fluid is good, and the electric control valve 200 and the overflow passage 300 are not needed. Therefore, the electric control valve 200 is in a closed state. Then, the magnetorheological fluid passes through the damping piston 130 in its entirety, and the damping force of the magnetorheological shock absorber is generated by the damping piston 130.

[0150] When the temperature T of the magnetorheological shock absorber is less than 0℃, it is defined that the magnetorheological shock absorber is in a low temperature state. At this time, the flowability of the magnetorheological fluid is poor, and the electric control valve 200 and the overflow passage 300 are needed. Therefore, different openings of the electric control valve 200 are matched by matching the temperature data of the magnetorheological shock absorber, the current data of the damping piston 130, and the driving state data of the vehicle.

[0151] As shown in FIG. 8, when the magnetorheological shock absorber is in a low temperature state, the temperature interval is divided into four temperature intervals of low temperature a, low temperature b, low temperature c, and low temperature d. When the temperature T of the magnetorheological shock absorber satisfies 0℃>T≥-10℃, it is defined that the temperature T of the magnetorheological shock absorber is in the temperature interval of low temperature a. When the temperature T of the magnetorheological shock absorber satisfies -10℃>T≥-20℃, it is defined that the temperature T of the magnetorheological shock absorber is in the temperature interval of low temperature b. When the temperature T of the magnetorheological shock absorber satisfies -20℃>T≥-30℃, it is defined that the temperature T of the magnetorheological shock absorber is in the temperature interval of low temperature c. When the temperature T of the magnetorheological shock absorber satisfies -30℃>T, it is defined that the temperature T of the magnetorheological shock absorber is in the temperature interval of low temperature d.

[0152] In the process of vehicle driving, the temperature data of the MR shock absorber is acquired, and it is determined whether the MR shock absorber is in a low temperature state. If yes, it is determined in which temperature interval the temperature of the MR shock absorber is, and the current data of the damping piston 130 is also acquired. At this time, the control device of the vehicle acquires the driving duration of the vehicle in the temperature interval of the temperature data by timing operation. Then, it is determined whether the driving duration is accumulated to the first set duration. If yes, it indicates that the temperature of the MR shock absorber is increased by a certain value, and the opening degree of the electric control valve 200 can be adjusted according to the current-opening degree curve of the previous temperature interval.

[0153] It can be understood that, as shown in FIG. 9, when the current of the damping piston 130 is constant, the temperature interval of low temperature rises to the temperature interval of high temperature, the flowability of the MR fluid becomes relatively good, and then the opening degree of the electric control valve 200 becomes smaller. For example, when the current of the damping piston 130 is 1A, the temperature interval of low temperature d jumps to the temperature interval of low temperature c, and then the opening degree of the electric control valve 200 is adjusted according to the current-opening degree curve corresponding to the temperature interval of low temperature c. At this time, compared with the temperature interval of low temperature d, the opening degree of the electric control valve 200 is reduced.

[0154] As shown in FIGS. 8 and 9, in the present embodiment, the first set duration is set to 10 min. For example, in the process of vehicle driving, when it is determined that the temperature of the MR shock absorber is lower than -30℃ and is in the temperature interval of low temperature d, the opening degree of the electric control valve 200 is adjusted according to the current-opening degree curve corresponding to the temperature interval of low temperature d.

[0155] Moreover, the timing starts from the determination that the MR shock absorber is in the temperature interval of low temperature d, and when the driving duration of the vehicle reaches 10 min, that is, the duration of the opening degree adjustment according to the current-opening degree curve corresponding to the temperature interval of low temperature d reaches 10 min, the state of the MR shock absorber will jump from the temperature interval of low temperature d to the temperature interval of low temperature c, and the opening degree adjustment of the electric control valve 200 is completed according to the current-opening degree curve corresponding to the temperature interval of low temperature c.

[0156] At the same time, the timing starts from entering the temperature interval of low temperature c, and when the driving duration of the vehicle reaches 10 min, the state of the MR shock absorber will jump again from the temperature interval of low temperature c to the temperature interval of low temperature b, and so on.

[0157] It can be understood that, after the vehicle is braked and decelerated and is in a stopped state, the calculation of the driving duration of the vehicle is paused, and when the vehicle drives again, the calculation of the driving duration is continued, and it is determined whether the driving duration reaches the first set duration. In this process, the vehicle speed data collected by the wheel speed sensor is accumulated in the duration when the vehicle speed data is not zero.

[0158] Further, as shown in FIG. 7, the step S32, i.e. the step of controlling the opening of the electric control valve 200 according to the current-opening curve, further includes the following steps:

[0159] Step S324: obtaining the driving time length of the vehicle when the temperature data of the vehicle is in the first temperature interval.

[0160] Step S325: judging whether the driving time length reaches the second set time length.

[0161] Step S326: if yes, controlling the electric control valve 200 to close.

[0162] It can be understood that the second set time length can be set according to actual conditions, which is not specifically limited here.

[0163] As shown in FIG. 8 and FIG. 9, in the present embodiment, the second set time length is also set to 10 min. For example, during the driving of the vehicle, when it is judged that the temperature of the MR damper is in the low temperature a temperature interval, the opening of the electric control valve 200 is controlled according to the current-opening curve corresponding to the low temperature a temperature interval.

[0164] Moreover, the time is counted since it is judged that the MR damper is in the low temperature a temperature interval, and when the driving time length of the vehicle reaches 10 min, the state of the MR damper will be jumped from the low temperature a temperature interval to the normal temperature state, at this time, the electric control valve 200 is controlled to close.

[0165] Since the MR damper is continuously heated and the temperature rises with the time of the vehicle movement, the opening of the electric control valve 200 can be controlled according to the driving time length of the vehicle and the current-opening curve of different temperature intervals, so that the electric control valve 200 and the overflow passage 300 gradually exit from the use state and remain in the standby state, effectively saving the electric energy.

[0166] As shown in FIG. 1 to FIG. 3, the vehicle according to the fourth aspect embodiment of the present application comprises the MR damper according to the first aspect embodiment, or comprises the control system of the MR damper according to the second aspect embodiment.

[0167] It can be understood that the MR damper is installed on the chassis of the vehicle, and specifically, the MR damper is arranged on the suspension system so as to play a damping role. In the control system of the MR damper, the temperature sensor is installed on the cylinder barrel 120 or the bracket arranged on the suspension system, so that the temperature sensor can obtain the temperature data of the MR damper.

[0168] The magnetorheological damper or the control system thereof is installed on a vehicle, and when the vehicle is in a running state, if the temperature of the magnetorheological damper is too low to cause poor fluidity of the magnetorheological fluid, the flow of the magnetorheological fluid in the damping piston 130 is reduced by opening the electric control valve 200, so that the damping force of the magnetorheological damper is reduced, and the maximum damping force and the adjustment multiple of the magnetorheological damper are effectively avoided from being reduced, so that the magnetorheological damper can play a good damping role.

[0169] Specifically, the vehicle can be a private car, such as a sedan, an SUV, an MPV, a pickup truck, or the like. The vehicle can also be an operating vehicle, such as a van, a bus, a small truck, or a large trailer, etc. The vehicle can be a gasoline vehicle or a new energy vehicle. When the vehicle is a new energy vehicle, it can be a hybrid vehicle or a pure electric vehicle.

[0170] As shown in FIGS. 4-7 and 10, the electronic device according to the fifth aspect of the present application comprises at least one processor, a memory, an input / output interface, a communication interface, and a bus. The memory stores a computer program executable by the at least one processor, and the computer program is executed by the at least one processor to enable the at least one processor to perform the control method of the magnetorheological damper according to the third aspect of the present application. The memory, the at least one processor, the input / output interface, and the communication interface are communicatively connected to each other within the device through the bus.

[0171] It can be understood that the processor can be implemented in the form of a general-purpose CPU (Central Processing Unit), a microprocessor, or one or more integrated circuits, etc., for executing related computer programs to implement the control method of the magnetorheological damper according to the third aspect of the present application.

[0172] The memory mainly includes a program storage area and a data storage area, wherein the program storage area can store an operating system and application programs required by at least one function; the data storage area can store data created according to the use of the terminal, etc. In addition, the memory can include a high-speed random access memory, and can also include a non-volatile memory, such as at least one magnetic disk storage device, a flash memory device, or other non-volatile solid-state storage device. In some examples, the memory can further include a memory remotely arranged with respect to the processor, which can be connected to the device through a network. Examples of the above-mentioned network include but are not limited to the Internet, an intranet, a local area network, a mobile communication network, and a combination thereof.

[0173] The input / output interface is used to connect the input / output unit to realize information input and output. The input / output unit can be arranged in the device as a component, or can be externally connected to the device to provide corresponding functions. The input unit can include a touch screen, a microphone, etc., and the output unit can include a display, a speaker, etc.

[0174] The communication interface is used to connect a communication unit to realize the communication interaction between the device and other devices. The communication unit can realize the communication function through wired or wireless mode. The bus includes a channel for transmitting information between various components of the device, such as the processor, the memory, the input / output interface and the communication interface.

[0175] As shown in FIGS. 4 to 7, the computer readable storage medium according to the sixth aspect of the present application has a computer program stored thereon, and the program is executed by a processor to realize the control method of the magneto-rheological damper according to the third aspect of the present application.

[0176] The computer readable storage medium of the embodiments of the present application can adopt any combination of one or more computer readable media. The computer readable medium can be a computer readable signal medium or a computer readable storage medium. The computer readable storage medium can be, but is not limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, device or apparatus, or any combination of the above. More specific examples (non-exhaustive list) of the computer readable storage medium include an electrical connection having one or more wires, a portable computer diskette, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above. In the embodiments of the present application, the computer readable storage medium can be any tangible medium containing or storing a program that can be used by or in conjunction with an instruction execution system, device or apparatus.

[0177] The computer readable signal medium can include a data signal carried in a baseband or as a part of a carrier wave, in which a computer readable program code is carried. Such a propagated data signal can take any of a variety of forms, including but not limited to electro-magnetic, optical, or any suitable combination thereof. The computer readable signal medium can also be any computer readable medium that is not a computer readable storage medium and that can be used to carry or store a program for use by or in connection with an instruction execution system, apparatus or device.

[0178] The program code contained in the computer readable medium can be transmitted by any suitable medium, including but not limited to wireless, wire, optical cable, RF, etc., or any suitable combination of the above.

[0179] In the description of the specification, reference to "one embodiment", "some embodiments", "an exemplary embodiment", "an example", "a specific example", or "some examples" means that a particular feature, structure, material, or characteristic being described is included in at least one embodiment or example of the application. The appearances of the phrases "in one embodiment", "in some embodiments", "in an exemplary embodiment", "an example", "a specific example", or "some examples" in various places in the specification are not necessarily referring to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0180] Although embodiments of the application have been shown and described, it will be appreciated that those skilled in the art can make various changes, modifications, substitutions and alterations thereto without departing from the principles and scope of the application, which are defined by the claims and their equivalents.

Claims

1. Magneto-rheological damper, characterized in that include: The main body of the monotube shock absorber includes a cylinder and a damping piston. The cylinder has a liquid cavity for containing magnetorheological fluid. The damping piston is disposed in the liquid cavity and divides the liquid cavity into a first cavity and a second cavity that are connected to each other. An overflow channel, one end of which is connected to the first cavity and the other end of which is connected to the second cavity; An electrically controlled valve is located on the overflow channel.

2. The magneto-rheological damper according to claim 1, characterized in that The electrically controlled valve is a solenoid valve.

3. The magneto-rheological damper according to claim 1, wherein, The electrically controlled valve includes: The valve seat has a valve cavity and a first valve port and a second valve port communicating with the valve cavity. The first valve port is communicating with the first cavity, and the second valve port is communicating with the overflow channel. The valve core is located inside the valve cavity; A return spring, one end of which is connected to the valve seat and the other end of which is connected to the valve core, is configured to drive the valve core to approach and block the first valve port; A coil winding is disposed on the valve seat and configured to magnetically attract the valve core when energized, so as to move the valve core away from and open the first valve port.

4. The magneto-rheological damper according to claim 3, characterized in that The valve seat includes a housing, an end cap, and a fixed seat; the housing and the end cap are connected and together form the valve cavity; the end cap is provided with the first valve port; the fixed seat is disposed in the valve cavity and is fixedly connected to the housing; the coil winding is disposed on the fixed seat; and one end of the return spring is connected to the fixed seat.

5. The magneto-rheological damper according to claim 4, characterized in that The fixed seat has a guide groove on the side facing the valve core, the valve core has a guide part on the side facing the fixed seat, the guide part has a limiting groove, the outer peripheral surface of the guide part contacts the inner peripheral surface of the guide groove, one end of the return spring abuts against the bottom of the guide groove, and the other end abuts against the bottom of the limiting groove.

6. Control system for a magneto-rheological damper, characterized in that include: The magnetorheological damper as described in any one of claims 1 to 5; A temperature sensor is configured to acquire temperature data of the magnetorheological damper; The control device is electrically connected to the temperature sensor and the magnetorheological damper, respectively, and is configured to control the electric valve to open when the temperature data is lower than the set temperature.

7. The control system of a magneto-rheological damper according to claim 6, characterized in that, The control device includes a vehicle controller and a chassis domain controller. The vehicle controller is configured to acquire vehicle driving status data and send it to the chassis domain controller. The chassis domain controller is configured to acquire the current data of the damping piston and control the opening degree of the electronically controlled valve based on the driving status data, the temperature data, and the current data.

8. The control system of a magneto-rheological damper according to claim 7, characterized in that, The chassis domain controller is configured to reduce the opening degree of the electronically controlled valve when the temperature data is lower than the set temperature and the vehicle is in motion, based on the increase in the current data.

9. A control method of a magneto-rheological damper, characterized by, The application of the magnetorheological vibration damper as described in any one of claims 1 to 5 includes the following steps: When the vehicle is in motion, acquire the temperature data of the magnetorheological damper; Determine whether the temperature data is lower than the set temperature; If so, control the solenoid valve to open; If not, control the electronically controlled valve to close.

10. The control method of the magneto-rheological damper according to claim 9, characterized by, If so, controlling the opening of the electrically controlled valve includes the following steps: If so, obtain the current data of the damping piston; According to the current-opening curve, the opening of the electrically-controlled valve is controlled; wherein on the current-opening curve, the greater the current data is, the smaller the opening of the electrically-controlled valve is.

11. The control method of the magneto-rheological damper according to claim 10, characterized by, The step of controlling the opening of the electrically-controlled valve according to the current-opening curve comprises the following steps: Obtaining the driving duration of the vehicle when the temperature data is in the ith temperature interval; wherein the temperature intervals are provided with n, the temperature of the mth temperature interval is higher than the temperature of the (m+1)th temperature interval, m, n and i are natural numbers, and n>1, 1 Determining whether the driving duration reaches a first set duration; If yes, the opening of the electrically-controlled valve is controlled according to the current-opening curve of the (i-1)th temperature interval.

12. The control method of the magneto-rheological damper according to claim 11, wherein The step of controlling the opening of the electrically-controlled valve according to the current-opening curve further comprises the following steps: Obtaining the driving duration of the vehicle when the temperature data is in the first temperature interval; Determining whether the driving duration reaches a second set duration; If yes, the electrically-controlled valve is controlled to be closed.

13. Vehicle, characterized in that The control system of the magneto-rheological damper comprises the magneto-rheological damper according to any one of claims 1 to 5, or the magneto-rheological damper according to any one of claims 6 to 8.

14. An electronic device, comprising: It comprises: at least one processor; and a memory connected with the at least one processor in communication; wherein the memory stores a computer program which can be executed by the at least one processor, and the computer program is executed by the at least one processor to enable the at least one processor to execute the control method of the magneto-rheological damper according to any one of claims 9 to 12.

15. A computer readable storage medium having stored thereon a computer program, characterized in that, The program is executed by the processor to implement the control method of the magneto-rheological damper according to any one of claims 9 to 12.

Images