CN206904139U - A kind of MR damper with multiple road conditions vibration control - Google Patents

Abstract

The utility model discloses a magneto-rheological damper with multi-road condition vibration control, which mainly consists of a composite left end cover, a damping cylinder body I, a damping cylinder body II, a reset spring, a composite right end cover, a vibration control excitation coil I, Piston head, vibration control excitation coil II, vibration control excitation coil III, etc. When the vibration control excitation coil II is energized, the pressure difference between the chamber I and the chamber III is not large, and the output damping force is not large. With the increase of the number of excitation coils, the pressure difference between the chamber I and the chamber III also increases. It will increase, and the output damping force will also increase accordingly. According to different road conditions, the output of three-stage damping force can be effectively realized, which is especially suitable for the vibration reduction system of automobile suspension.

Description

A magneto-rheological damper with multi-road condition vibration control

technical field

The utility model relates to a magneto-rheological damper, in particular to a magneto-rheological damper with multi-road condition vibration control.

Background technique

The characteristics of millisecond-level response speed, large control range and large damping force output of the magneto-rheological damper make it an excellent semi-active actuator in the field of industrial applications. At present, magnetorheological dampers have been widely used in the vibration reduction of rolling stock and automobile suspension systems. When the magnetorheological damper is working, the flow channel of the magnetorheological fluid is often set on a closed circuit with a controllable magnetic field. When the piston of the damper moves relative to the cylinder, the magnetorheological fluid flows in the flow channel, and through the control The excitation magnetic field acting on the magnetic flux circuit can change the shear stress of the magnetorheological fluid and realize the stepless adjustment of the output damping force of the damper.

In the traditional magneto-rheological damper, usually only one damping excitation coil is set on the piston head to control the damping force of the magneto-rheological fluid channel. The controls are adequate. However, in deserts or mountains, with the increase of vibration frequency and amplitude, the viscous damping force becomes larger, and the automobile suspension with a single damping excitation coil has better performance in terms of controllable damping force, controllable damping ratio and controllable speed range. It can no longer meet the demand, such as armored vehicle suspension system, off-road vehicle suspension system, etc., which are generally achieved by sacrificing the controllable damping force of the magneto-rheological damper and increasing the length of the effective damping channel by increasing the volume of the device. This limits the application range of magneto-rheological dampers.

Therefore, it is necessary to design a new type of magnetorheological damper, which neither reduces the output controllable damping force nor increases it, thereby improving the performance of the magnetorheological damper.

Contents of the invention

In order to overcome the problems existing in the background technology and to meet the actual use requirements of the magnetorheological damper, the utility model proposes a magnetorheological damper with multi-road condition vibration control. A damping cylinder II with two grooves is installed in the piston head of a conventional valve damper, which is used to place the vibration control excitation coil I and the vibration control excitation coil III, and at the same time forms a valve damping channel with the damping cylinder I , A return spring is placed between the piston head and the right end cover in the ordinary. When the damping excitation coil is not energized, the liquid flow channel is fully open without any hindrance, and can move freely in the axial direction, and the piston on the car suspension returns to its original position by spring deformation; when the car is driving on an ordinary road, the car Due to its own gravity and road surface conditions will produce small amplitude vibration, the vibration control excitation coil II in the piston head is energized, and at this time, two sections of damping are formed in the liquid flow channel, and the pressure difference between the closed cavity I and the closed cavity III is not large, so The output damping force is not large; when the car is driving on an uneven road, the suspension of the car will vibrate strongly due to the uneven road surface. At this time, only energizing the vibration control excitation coil II in the piston head is not enough to offset the closed volume I The vibration caused by the pressure difference with the closed chamber III, at this time, the vibration control excitation coil II and the vibration control excitation coil I are energized at the same time, in the liquid

The flow channel is divided into four stages of damping, and the pressure difference between the closed volume I and the closed volume III becomes twice the original, so the vibration can be offset; In severe vibration, at this time, the vibration control excitation coil Ⅰ, vibration control excitation coil Ⅱ and vibration control excitation coil Ⅲ are energized at the same time, and six sections of damping are formed in the liquid flow channel to offset the pressure difference between the closed volume chamber Ⅰ and the closed volume chamber Ⅲ. vibration. This structural design provides a three-stage damping force output by restricting the flow channel of the magnetorheological fluid. On the premise of not increasing the length of the damping gap and the current, it can provide a larger output damping force, and is especially suitable for automobile suspensions for multi-road condition vibration control.

The technical solution adopted by the utility model to solve its technical problems includes: piston rod (1), composite left end cover (2), damping cylinder body I (3), damping cylinder body II (4), return spring (5), Composite right end cover (6), vibration control excitation coil I (7), piston head (8), vibration control excitation coil II (9), vibration control excitation coil III (10); composite left end cover (2) intermediate processing There is a circular through hole, the piston rod (1) is in clearance fit with the inner surface of the composite left end cap (2), and the piston rod (1) and the inner surface of the composite left end cap (2) are sealed by a sealing ring; the composite left end cap ( 2) It is fixedly connected with the left end faces of damping cylinder Ⅰ (3) and damping cylinder Ⅱ (4) respectively through screws, and the composite left end cover (2) is connected with damping cylinder Ⅰ (3) and damping cylinder Ⅱ (4) The sealing ring is used to seal between them; the composite left end cover (2) is provided with two radially arranged counterbore grooves, the composite right end cover (6), damping cylinder body I (3), damping cylinder body II (4) The connection is fixed by screws and sealed by a sealing ring; the right end of the piston rod (1) is processed with an external thread; the center of the piston head (8) is processed with a through hole, and the piston rod (1) and the piston head (8) are machined with steps for interference Cooperate; the piston rod (1) and the piston head (8) are tightly connected by nuts; a return spring (5) is installed between the piston head (8) and the composite right end cover (6); rheological fluid; damping cylinder II (4) is provided with 8 circular damping passages for magnetorheological fluid to pass through; damping cylinder II (4) is processed with two grooves, vibration control excitation coil I ( 7) and the vibration control excitation coil III (10) are respectively wound on the groove of the damping cylinder II (4), and the lead wire is drawn out from the lead hole on the damping cylinder II (4); the concave hole on the outer surface of the piston head (8) In the groove, two lead wires are led out through the lead wire hole of the piston rod (1); the damper is installed in the automobile suspension. Vibration control excitation coil I (7), vibration control excitation coil II (9) and vibration control excitation coil III (10) constitute a three-stage vibration control excitation coil; when the piston rod vibrates caused by general plain roads, the vibration control excitation coil When Ⅱ (9) is energized, the viscosity of the magnetorheological fluid becomes lower, forming a section of damping to attenuate the vibration of the piston rod; when the vibration of the piston rod is caused by the road with serious road damage, the vibration control excitation coil Ⅱ (9) and the vibration control The excitation coil Ⅰ (7) is energized at the same time, and two sections of effective damping in series are generated in the damping channel, and the vibration of the piston rod attenuates rapidly; The coil I (7) and the vibration control excitation coil III (10) are energized at the same time, the magnetorheological fluid is magnetized to form three effective series damping, and the vibration of the piston rod is rapidly attenuated. Composite left end cover (2), piston head (8), and damping cylinder I (3) form a cavity I; damping cylinder I (3), damping cylinder II (4), composite left end cover ( 2) and the composite right end cover (6) enclose chamber II; piston head (8), damping cylinder body I (3), and composite right end cover (6) enclose chamber III; when the piston rod (1 ) stretches along the axial direction, the magneto-rheological fluid in chamber I enters chamber II and chamber III sequentially through the damping channel; when the piston rod (1) is compressed along the axial direction, the magnetorheological fluid in chamber III The magnetorheological fluid enters chamber II and chamber I sequentially through the liquid flow channel; when the piston rod (1) moves in the axial direction, the volumes of chamber I and chamber III will change, and the return spring (5) springs Deformation, at this time the spring will achieve the balance of the piston position through the axial contraction movement.

Compared with the background technology, the utility model has the beneficial effects of:

(1), the magnetorheological damper of the utility model realizes the vibration reduction function in different occasions by controlling the number of exciting coils electrified under the condition that the first exciting coil is normally energized and the energized current is constant; When driving on ordinary roads, it is only necessary to energize the vibration control excitation coil II in the piston head; when driving on an uneven road, it is necessary to simultaneously energize the vibration control excitation coil II and the vibration control excitation coil I at the same time to meet the requirements of the vehicle suspension. Vibration control; when the car is driving on a mountain road, the control excitation coil Ⅰ, vibration control excitation coil Ⅱ and vibration control excitation coil Ⅲ must be energized at the same time to form six sections of damping to offset the vibration of the suspension; as the number of energized Increase the output damping force to double, and form a three-stage vibration reduction to adapt to different occasions; on the premise of not increasing the longitudinal length and volume of the damper, it can provide a larger output damping force, especially suitable for multi-road condition vibration control car suspension.

The parts damping cylinder body I (3), damping cylinder body II (4) and piston head (8) used in the magnetorheological damper of the utility model are respectively made of low-carbon steel magnetic materials; the rest of the parts are made of non-magnetic materials production. This design gives full play to the effect of the vertical magnetic field on the magneto-rheological fluid, and also allows the return spring (5) to shrink to achieve vibration control.

Description of drawings

Fig. 1 is the structural representation of the utility model.

Fig. 2 is a schematic diagram of the magnetorheological fluid flowing through the liquid flow channel when the piston rod of the utility model is stretched.

Fig. 3 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the first working state of the present invention.

Fig. 4 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the second working state of the present invention.

Fig. 5 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the third working state of the present invention.

Fig. 6 is a side view of the left end cover of the piston head of the present invention.

Fig. 7 is a side view of the right end cover of the piston head of the present invention.

detailed description

Below in conjunction with accompanying drawing and embodiment the utility model is further described:

As shown in Figure 1, the utility model includes: a piston rod (1), a composite left end cover (2), a damping cylinder I (3), a damping cylinder II (4), a return spring (5), a composite right end Cover (6), vibration control excitation coil I (7), piston head (8), vibration control excitation coil II (9), vibration control excitation coil III (10).

Fig. 2 is a schematic diagram of the magnetorheological fluid flowing through the liquid flow channel when the piston rod of the utility model is stretched. Among them, the composite left end cover (2), the piston head (8), and the damping cylinder I (3) form a cavity I; the damping cylinder I (3), the damping cylinder II (4), and the composite left end The cover (2) and the composite right end cover (6) form a chamber II; the piston head (8), the damping cylinder body I (3), and the composite right end cover (6) form a chamber III; when the piston rod (1) When stretching along the axial direction, the magnetorheological fluid in chamber I enters chamber II and chamber III sequentially through the damping channel; when the piston rod (1) is compressed in the axial direction, chamber III The magnetorheological fluid inside enters the chamber II and the chamber I sequentially through the liquid flow channel.

Fig. 3 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the first working state of the present invention. When the vibration control excitation coil II (9) in the piston head is energized, the closed magnetic field formed by the damping cylinder I (3), the damping cylinder II (4) and the piston head will form two stages of liquid flow damping in the liquid flow channel, The vibration caused by the pressure difference between the closed chamber I and the closed chamber III is small, and the output damping force is small.

Fig. 4 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the second working state of the present invention. When the vibration control excitation coil II and the vibration control excitation coil I are energized at the same time, the closed magnetic field formed by the damping cylinder I (3), the damping cylinder II (4) and the piston head will form four stages of liquid flow damping in the liquid flow channel. The liquid flow channel is formed into four stages of liquid flow damping, the pressure difference between the closed chamber I and the closed chamber III becomes twice the original, and the vibration is aggravated, so a larger damping force can be output.

Fig. 5 is a schematic diagram of the distribution of magnetic lines of force and the effective damping gap in the third working state of the present invention. Simultaneously energize the vibration control excitation coil Ⅰ, vibration control excitation coil Ⅱ and vibration control excitation coil Ⅲ, and the closed magnetic field formed by the damping cylinder Ⅰ (3), damping cylinder Ⅱ (4) and the piston head travels in the liquid flow channel into six sections Liquid flow damping, six sections of damping are formed in the liquid flow channel to offset the vibration caused by the pressure difference between the closed chamber I and the closed chamber III.

Fig. 6 is a sectional view of the damping cylinder I (3) of the present invention. Among them, four waist-shaped through holes uniformly arranged in the circumferential direction are respectively processed at the positions corresponding to the liquid flow channels at both ends of the damping cylinder body I (3). When the damper is working, this design can make the liquid flow channel form a whole, which is used for the flow channel of the magneto-rheological fluid to enter and exit; to realize the control of vibration and the reset of the piston head.

Fig. 7 is a sectional view of the damping cylinder II (4) of the utility model. The outer surface of the damping cylinder II (4) is processed with two grooves for controlling the magnitude of the output damping force when electrified.

The working principle of the utility model is as follows:

As shown in Figure 1, Figure 2, Figure 3, Figure 4 and Figure 5, when the vibration control excitation coil II (9) in the piston head (8) is energized, the damping cylinder I (3), damping cylinder II (4) and the closed magnetic field formed by the piston head (8) run in the liquid flow channel to form two stages of liquid flow damping, the vibration caused by the pressure difference between the closed chamber I and the closed chamber III is small, and the output damping force is small. When the vibration control excitation coil II and the vibration control excitation coil I are energized at the same time, the closed magnetic field formed by the damping cylinder I (3), the damping cylinder II (4) and the piston head (8) travels in the liquid flow channel into four sections of liquid flow Damping, four stages of liquid flow damping are formed at the liquid flow channel, the pressure difference between the closed chamber I and the closed chamber III becomes twice the original, and the vibration is aggravated, so a larger damping force can be output. Simultaneously energize vibration control excitation coil Ⅰ, vibration control excitation coil Ⅱ and vibration control excitation coil Ⅲ, the closed magnetic field formed by damping cylinder Ⅰ (3), damping cylinder Ⅱ (4) and piston head (8) will flow in the liquid flow channel. Six stages of liquid flow damping are formed in the liquid flow channel to offset the vibration caused by the pressure difference between the closed chamber I and the closed chamber III.

Claims (3)

1. A kind of 1. MR damper with multiple road conditions vibration control, it is characterised in that including：Piston rod (1), combined type are left End cap (2), resistance cylinders I (3), resistance cylinders II (4), back-moving spring (5), combined type right end cap (6), vibration control excitation wire Enclose I (7), piston head (8), vibration control magnet exciting coil II（9）, vibration control magnet exciting coil III (10)；Combined type left end cap (2) Centre is machined with manhole, and piston rod (1) coordinates with combined type left end cap (2) internal surface gaps, piston rod (1) and combined type Left end cap (2) inner surface is sealed by sealing ring；Combined type left end cap (2) and resistance cylinders I (3) and resistance cylinders II (4) left side is fixedly connected by screw respectively, combined type left end cap (2) and resistance cylinders I (3), resistance cylinders II (4) it Between sealed by sealing ring；Counterbore groove of the combined type left end cap (2) provided with two radial arrangements, combined type right end cap (6), Resistance cylinders I (3), resistance cylinders II (4) are fixedly connected by screw, are sealed by sealing ring；Piston rod (1) right-hand member adds Work has external screw thread；Piston head (8) center is machined with through hole, and the piston rod (1) and piston head (8) for being machined with step are interference fitted； Piston rod (1) is fastenedly connected with piston head (8) by nut；Equipped with reset between piston head (8) and combined type right end cap (6) Spring (5)；Damper cavity is built with magnetic flow liquid；Resistance cylinders II (4) are provided with 8 annulars passed through for magnetic flow liquid Damp channel；Two grooves, vibration control magnet exciting coil I (7) and vibration control magnet exciting coil are machined with resistance cylinders II (4) III (10) are respectively wound around on the groove of resistance cylinders II (4), and lead is drawn from the fairlead on resistance cylinders II (4)；Piston In the groove of head (8) outer surface, two leads are drawn by the fairlead of piston rod (1)；Damper is arranged in automotive suspension.
2. A kind of 2. MR damper with multiple road conditions vibration control according to claim 1, it is characterised in that：Vibration Control magnet exciting coil I（7）, vibration control magnet exciting coil II (9), vibration control magnet exciting coil III (10) form three-level vibration control Magnet exciting coil；When piston rod caused by general Plain road vibrates, it is powered to vibration control magnet exciting coil II (9), it is magnetorheological Fluid viscosity step-down, forming one section of damping makes piston rod vibration decay；Shaken when in piston rod caused by the serious road of road damage When dynamic, to vibration control magnet exciting coil II (9) and vibration control magnet exciting coil I（7）It is powered simultaneously, series connection is produced in damp channel Two sections of effective dampings, the rapid decay of piston rod vibration；When piston rod caused by rugged mountain path vibrates, encouraged to vibration control Magnetic coil II (9), vibration control magnet exciting coil I（7）It is powered simultaneously with vibration control magnet exciting coil III (10), magnetic flow liquid magnetic Change and form three sections of effective series dampeds, the rapid decay of piston rod vibration.
3. 3. a kind of MR damper with multiple road conditions vibration control according to claim 1,

   It is characterized in that：Cavity volume I is surrounded between combined type left end cap (2), piston head (8), resistance cylinders I (3)；Resistance cylinders I (3), resistance cylinders II (4), combined type left end cap (2) and combined type right end cap (6) surround cavity volume II；Piston head (8), damped cylinder Body I (3), combined type right end cap surround cavity volume III between (6)；When piston rod (1) extensional motion vertically, the magnetic in cavity volume I Rheology liquid sequentially enters cavity volume II and cavity volume III by damp channel；When piston rod (1) is in axial direction compressed, cavity volume III Interior magnetic flow liquid sequentially enters cavity volume II and cavity volume I by fluid course；When piston rod (1) in axial direction moves, cavity volume I It can be changed with the volume of cavity volume III, back-moving spring (5) spring is deformed, and now spring can pass through the contractile motion of axial direction To realize the balance of piston position.