JP2004092832A - Magnetic spring mount device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a magnetic spring mount device for supporting a heavy cargo by the resultant force of a spring force and a magnet force. <P>SOLUTION: This magnetic spring mount device 1 for supporting the heavy cargo (engine 6) by the resultant force of the spring force and magnet force comprises a first member (body case) 3 mounted with a movable first magnet 5; second members (support plate and rod) 7 and 8 arranged movably to the first member through a spring member 10, and mounted with a second magnet 9 in a position corresponding to the first magnet; a drive motor 22 for moving the first magnet of the first member; a control means (CPU) 21 for moving the first magnet of the first member with the heavy cargo (engine 6) being mounted on the second member so that the resultant force of the force of the spring member and the force by the first and second magnets is regularly substantially constant within a prescribed displacement range of the second members; and magnet locking means 22 and 29 for locking or unlocking the first magnet. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a magnetic spring mounting device, and more particularly to a magnetic spring mounting device that supports a heavy object by a combined force of a spring force and a magnet force.
[0002]
[Prior art]
Conventionally, as disclosed in, for example, Japanese Patent Application Laid-Open Nos. Hei 10-238585 and Hei 6-42385, a heavy object is supported by magnetic force of a magnet and vibrations from the heavy object are insulated. It has been known.
Further, utilizing the balance between the repulsive force of the spring and the attractive force of the magnet, the repulsive force of the entire system including the spring and the magnet (the repulsive force of the spring and the attractive force of the magnet) can be used to increase the displacement of the movable part. There is known a "magnetic-spring vibration isolation principle" in which the resultant force is kept constant, that is, the spring constant is substantially zero, and vibration is not transmitted (insulated).
[0003]
[Problems to be solved by the invention]
Next, this "principle of vibration isolation of a magnetic-spring system" will be described with reference to FIGS. Note that the magnetic spring mounting device shown in FIGS. 1 and 2 has been devised by the present inventors and is a device on which the present invention is based, and therefore does not fall under the prior art.
[0004]
FIG. 1A shows a state where only a static load is applied, and FIG. 1B shows a state where an excessive load (static load + dynamic load) is applied. As shown in FIG. 1, the magnetic spring mounting device 50 includes a main body case 52, a first magnet 54 attached to the main body case 52, and a heavy object (Weng) disposed concentrically inside the main body case 52. , A second magnet 58 attached to the movable member 56, and a spring member 60 for connecting the movable member 56 to the main body case 52 so as to be movable in the axial direction.
[0005]
FIG. 2 is a diagram showing a load-displacement characteristic of the magnetic spring mounting device 50. Now, assuming that the movable member 56 supports a heavy object (Weng) having a predetermined static load, the load-displacement characteristic of the spring member 60 is indicated by a broken line {circle around (1)}, and the load-displacement characteristic of the magnets 54 and 58 is shown. The characteristic is shown by a chain line (2), and the resultant force of both is as shown by a solid line (3). Here, the origin (0) of the displacement of the movable member 56 is a static balance position. This device effectively insulates the vibration against the vibration displacement around the origin (0) in FIG. 2 within the range (A) where the spring constant of the entire system including the spring and the magnet is 0. ing. However, this device has a problem that vibration is transmitted (vibration cannot be insulated) in other displacement regions (B).
[0006]
Further, due to its structure, when a load (static load + dynamic load) of a fixed value or more is applied to the magnetic spring mounting device 50 and the relative position between the first magnet 54 and the second magnet 58 changes significantly, both of them are changed. 1 (b), there is also a problem that even if the value of the dynamic load decreases, it does not return to the original position.
[0007]
These problems are particularly noticeable when the magnetic spring mount device is applied to an engine mount, a suspension mount of a car, a cab (cabin) mount of a truck or a construction machine, or the like. That is, in any case, due to the torque reaction force of the engine or the acceleration / deceleration (G) acting on the vehicle body when the vehicle is accelerating or decelerating, or due to the inertia force of the engine or the vehicle body when traveling on a curved road or a road with large undulations, Pitching of the engine and the vehicle body becomes large, and a large load (dynamic load) is applied to the magnetic spring mounting device. As a result, in the displacement region (B) other than the range (A) shown in FIG. The magnet 58 cannot return to its original position. In particular, since an automobile unit (engine or vehicle body) is heavy, the spring constant of a spring for supporting the automobile unit is large, and a very large vibration is transmitted outside the range (A).
[0008]
In order to solve these problems, it is conceivable to further expand the displacement region in the range (A) of FIG. 2. However, this increases the size of the entire device including the first magnet 54 and the second magnet 58, which is preferable. Absent. Furthermore, when supporting heavy objects such as automobile engines, it is necessary to use rare earth magnets that generate high magnetic force, and such magnets are very expensive, which makes it difficult to commercialize them in terms of cost. Exists.
The present invention has been made to solve the above-described problem, and provides a magnetic spring mount device that can effectively insulate vibration against a large load fluctuation without increasing the size of a magnet. It is an object.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, the present invention is a magnetic spring mount device for supporting a heavy object by a combined force of a force of a spring and a force of a magnet, wherein a first magnet movable in an axial direction is attached. A first member, a second member disposed relatively reciprocally with respect to the first member via a spring member, and a second magnet attached to a position corresponding to the first magnet; A magnet driving means for moving the first magnet of one member along the axial direction and a heavy object to be supported on the first member or the second member are attached, and the first magnet of the first member is moved by the magnet driving means. Control means for making the combined force of the force of the spring member and the force of the first and second magnets substantially constant within a predetermined displacement range of the second member; The distance in the axial direction exceeds the specified tolerance If hearing is, the first magnet lock, when it becomes smaller than the predetermined allowable value it is characterized by having a magnet locking means to unlock the first magnet, the.
[0010]
In the present invention configured as described above, even if a dynamic load due to a heavy object acts on the first member or the second member, and the second member is relatively displaced relative to the first member, the control means may be used. However, the first magnet of the first member is moved by the magnet driving means, so that the resultant force of the force of the spring member and the force of the first and second magnets is always substantially constant in a predetermined displacement range of the second member. Thus, the vibration from the second member can be always insulated from the first member (or the vibration from the first member from the second member). As a result, the first magnet and the second magnet can be reduced in size, and thus the entire device can be reduced in size.
Further, in the present invention, when the axial distance between the first magnet and the second magnet is larger than a predetermined allowable value, the first magnet is locked by the locking means, and the first magnet is reliably locked by the change in load. The distance between the first magnet and the second magnet can be returned within a predetermined allowable value. Further, when the value becomes smaller than the predetermined allowable value, the lock of the first magnet is released, and the control by the control means is executed.
[0011]
In the present invention, preferably, the magnet locking means electrically locks the magnet driving means.
In the present invention, preferably, the magnet locking means mechanically locks the magnet driving means.
[0012]
In the present invention, preferably, the magnet locking means locks the first magnet at a predetermined position.
In the present invention, preferably, the magnet locking means locks the first magnet when a predetermined large load acts on the first member or the second member.
[0013]
The present invention preferably further comprises alarm means for issuing an alarm when the first magnet is locked by the magnet locking means.
[0014]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 3 is a basic configuration diagram showing one embodiment of the magnetic spring mounting device of the present invention. This embodiment is an example in which the magnetic spring mounting device of the present invention is applied to an engine mount of an automobile.
As shown in FIG. 3, reference numeral 1 denotes a magnetic spring mounting device 1 according to the present embodiment, and the magnetic spring mounting device 1 is mounted on a vehicle 2. The magnetic spring mount device 1 has a main body case 3 fixedly arranged on a vehicle 2, a main body side movable magnet 5 as a first magnet mounted on the main body case 3 via a ball nut 4, and an engine 6. A support plate 7 for supporting the engine 6; a rod 8 attached to the support plate 7 and extending into the body case 3; a rod-side magnet 9 as a second magnet attached to a lower end of the rod 8; A spring 10 for connecting the case 3 and the support plate 7 to each other.
[0015]
The support plate 7 and the rod 8 can move up and down integrally along the axial direction 11. The body-side movable magnet 5 is movable in the axial direction 11 by a drive motor 22 described later.
In the present embodiment, the engine 6 to be supported is attached to the support plate 7 and the main body case 3 is fixed to the vehicle 2. On the contrary, the engine 6 to be supported is attached to the main body case 3. Alternatively, the support plate 7 may be fixed to the vehicle 2.
[0016]
The main body-side movable magnet 5 includes an N pole and an S pole, and an S pole is arranged on the upper side and below the N pole along the axial direction 11. Similarly, the rod-side magnet 9 has an N-pole on the upper side and an S-pole on the lower side in the axial direction 11. In the present embodiment, the magnets 5 and 9 use rare earth permanent magnets, but other permanent magnets such as alnico magnets and ferrite magnets, and further, electromagnets may be used. The arrangement of the north pole and the south pole in the magnets 5 and 9 is opposite to the illustrated one, and the main body side movable magnet 5 and the rod side magnet 9 have the S pole and the lower Alternatively, the N pole may be used.
[0017]
When the engine 6 is mounted on the support plate 7, the spring 10 bends in proportion to the weight of the engine 6. In the present embodiment, the spring 10 bends under the static load of the engine 6, and at this statically balanced position, as shown in FIGS. The boundary position of the S pole is set to coincide with the boundary positions of the N pole and the S pole of the rod-side magnet 9.
[0018]
FIG. 4A shows a state where only a static load is applied, and FIG. 4B shows a state where an excessive load (static load + dynamic load) is applied.
Next, the “load-displacement characteristic” when the magnetic spring mounting device 1 of the present embodiment is in the state of FIG. 4A will be described. The “load-displacement characteristic” of the magnetic spring mounting device 1 is the same as that shown in FIG. That is, as described above, in the load-displacement characteristic of FIG. 2, the load-displacement characteristic due to the spring 10 is indicated by a broken line {circle around (1)}, and the load-displacement characteristic due to the repulsion and attraction of the magnets 5 and 9 is indicated by a chain line {circle around (2)}. The resultant force of the two is indicated by a solid line (3).
[0019]
Here, the displacement is the amount of movement of the support plate 7 (including the rod 8) with respect to the main body case 3, and as shown in FIG. Is negative. The load is a force generated in the spring 10 or a force (repulsive force / attractive force) generated between the magnets 5 and 9 when the support plate 7 is displaced. The force trying to push it back is positive, and the force trying to pull it down is negative.
[0020]
Explaining in more detail with reference to FIG. 2, the static equilibrium position when the engine 6 is mounted is a position where the displacement = 0 (see FIG. 4A). At this time, the spring 10 generates a load W that balances with the engine weight Weng, but no load (repulsive force / attractive force) is generated between the magnet 5 and the magnet 9. When the displacement increases from the static balance position (displacement = 0), the load on the spring 10 increases in proportion to the increase in the displacement, and the slope of the broken line (1) becomes positive.
On the other hand, the load by the magnets 5 and 9 decreases in inverse proportion to the increase in the displacement, and the inclination of the chain line (2) becomes negative. Therefore, in the magnets 5 and 9, when the displacement increases from the static equilibrium position, the load shows a negative value, and a pulling force is generated. Further, when the displacement decreases from the static balance position, the load shows a positive value, and a force to push upward is exerted. That is, in the magnets 5 and 9, when the support plate 7 deviates from the static balance position, a force acts between the rod-side magnet 9 and the main body-side movable magnet 5 to move away from the static balance position.
[0021]
The load-displacement characteristic of the entire system including the spring and the magnet (magnetic spring mounting device 1) is shown by a solid line (3) in FIG. 2 which is a sum of the diagrams (1) and (2). In the present embodiment, the spring 10 is adjusted so that the absolute value of the load increase amount of the spring 10 with respect to the displacement (inclination of (1)) and the absolute value of the load decrease amount of the magnets 5 and 9 (inclination of (2)) are substantially equal. , The shapes, dimensions, gaps, etc. of the magnets 5 and 9 are set. As a result, the load-displacement characteristic ((3)) of the entire system including the spring 10 and the magnets 5 and 9 in the magnetic spring mounting device 1 shows that the load is maintained at a constant value as the displacement increases, and the spring constant is almost constant. It has a range A where it is zero.
In this range A, even if a vibration input within the range A is applied to one end of the magnetic spring mounting device 1, that is, the support plate 7 of the engine 6, the spring constant for this vibration input is 0. The excitation force is not transmitted to 3), and the excitation force is not transmitted to the vehicle 2 side.
[0022]
The magnetic spring mounting device 1 further includes a displacement sensor 12 for detecting a displacement of the support plate 7 with respect to the main body case 3 and a displacement sensor 13 for detecting a displacement of the main body side movable magnet 5 with respect to the main body case 3. Each of the displacement sensors 12 and 13 is connected to an I / F (interface) 20, and the I / F 20 is connected to a CPU 21. A drive motor 22 and a drive motor driver 23 for moving the movable magnet 5 along the axial direction 11 are connected to the CPU 21.
[0023]
The detection signals of the displacement sensors 12 and 13 are input to the CPU 21 via the I / F 20. The CPU 21 receives a steering angle signal, a vertical G signal of the vehicle, an accelerator opening from a steering angle sensor 24, a vehicle vertical G sensor 25, an accelerator opening sensor 26, a brake input sensor 27, and a vehicle speed sensor 28, respectively. A signal, a brake input signal and a vehicle speed signal are also input.
[0024]
The CPU 21 determines a later-described target displacement (Tr) of the main body side movable magnet 5 based on a signal from the displacement sensor 12, and outputs an output signal thereof to the drive motor driver 23. The driver 23 drives the drive motor 22 in response to a signal received from the CPU 21. The drive motor 22 moves (moves up and down) the movable magnet 5 along the axial direction 11 via the ball nut 4. Further, the displacement amount of the main body side movable magnet 5 detected by the displacement sensor 13 is input to the CPU 21 and feedback control is performed so that a target displacement is obtained.
[0025]
The drive motor 22 is a DC motor, but a stepping motor, a hydraulic motor, or the like may be used. When a stepping motor is used, the feedback displacement sensor 13 need not be provided. Further, the displacement amount of the main body side movable magnet 5 may be detected by attaching an encoder to the output shaft of the drive motor. Further, in order to prevent the motor from rotating by losing the magnetic force of the magnet, and to lock the movable magnet 5 in the lock position as described later (see FIG. 7), the position of the main body side movable magnet 5 is set. Is provided.
[0026]
As described above, since the main body side movable magnet 5 is moved along the axial direction, a large load is applied to the magnetic spring mount device 1 of the present embodiment, and the magnetic spring mount device 1 is not limited to the range shown in FIG. 2B, even if an engine vibration having a range and amplitude indicated by B is inputted, the main body-side movable magnet 5 is moved as shown in FIG. The range A in which the value is 0 shifts to the range A 'shown in FIG. 5, and the vibration in the range B can be isolated. Further, it is possible to prevent the rod-side magnet 9 from returning to the original static balance position (displacement = 0).
[0027]
Next, a method for determining the target displacement of the main body side movable magnet 5 will be described. The displacement detected by the displacement sensor 12 includes frequency components of various magnitudes. If the main body side movable magnet 5 is moved following all of the frequency components, the movable magnet 5 moves in synchronization with the magnet 9 as a result, which is not preferable. Therefore, in the present embodiment, the CPU 21 has a function of a low-pass filter, and determines the target displacement of the main body-side movable magnet 5 based on the displacement of the specific frequency component of the magnet 9. The reason why the low-pass filter is used is that the vibration input for increasing the relative displacement between the movable magnet 5 and the rod-side magnet 9 is relatively low with respect to the vibration frequency to be insulated.
[0028]
Generally, the characteristics of this low-pass filter are determined by a time constant. When the time constant is small, the frequency band is widened and follows a constant high-frequency component. On the other hand, the main body-side movable magnet 5 can reliably follow the rod-side magnet 9. On the other hand, when the time constant is large, the frequency band is limited to a relatively narrow region of low frequency, and although the followability of the main body side movable magnet 5 to the rod side magnet 9 is inferior, the vibration frequency component to be insulated is low. There is no following.
For example, when the load applied to the mount is considered to increase due to the torque reaction of the engine, such as during acceleration, the time constant is reduced to increase the followability, and the position of the main body side movable magnet 8 is changed to the rod side magnet. 9 can be surely moved, and the problem that the rod-side magnet 9 cannot return to the original position can also be prevented. On the other hand, when the load variation applied to the mount is not large, such as when traveling at a constant speed, it is possible to increase the time constant to reduce the followability and to effectively insulate the vibration frequency component to be insulated.
[0029]
Next, the control content (follow-up control) in the case of determining the target displacement and controlling the drive motor according to the present embodiment will be described with reference to the flowchart of FIG. In FIG. 6, S indicates each step.
First, in S1, the displacement X of the support plate 7 (engine) with respect to the main body case 3 detected by the displacement sensor 12 is input. Next, in S2, it is determined whether or not the steering angle is equal to or more than a predetermined value and equal to or more than a predetermined vehicle speed. If NO, the process proceeds to S3. Next, in S3, it is determined whether or not the vertical G of the vehicle is equal to or more than a predetermined value. If NO, the process proceeds to S4. Next, in S4, it is determined whether or not the throttle is turned on when the vehicle is stopped (the accelerator pedal is depressed), and if NO, the process proceeds to S5. Next, in S5, it is determined whether or not the vehicle is accelerating or decelerating at a predetermined value or more based on the accelerator opening or the brake signal. If NO, the process proceeds to S7.
[0030]
In S7, the time constant is set to T2. The time constant T2 is a value larger than the time constant T1 described later. Here, it is considered that the time constant T2 (> T1) is set in such a manner that the load acting on the magnetic spring mount device 1 does not largely change and the vibration center displacement thereof does not largely change in the above-described vehicle driving state. Therefore, by increasing the time constant, the ability of the main body side movable magnet 5 to follow the displacement of the support plate 7 (engine 10) is reduced, and the vibration can be effectively generated without following the vibration frequency component to be insulated. This is for insulation. This ensures that the vibration of the engine is transmitted to the vehicle during idling or when the vehicle is traveling at a constant speed such that the load variation is small and the vibration input range is maintained in the range of A in FIG. Thus, the vibration noise perceived by the occupant is reduced satisfactorily.
[0031]
On the other hand, if it is determined in S2 that the steering angle is equal to or greater than the predetermined value and equal to or greater than the certain speed, the process proceeds to S6, and the time constant is set to T1. The time constant T1 is a value smaller than the time constant T2. In this case, it is considered that the vehicle is traveling on a curve, and the load acting on the magnetic spring mounting device increases due to the inertial force of the vehicle body and the engine, and the relative positions of the magnets 5 and 9 fluctuate. There is a possibility that a problem may occur such that the input is performed in a range (range B) other than the range A, and the rod-side magnet 9 does not largely deviate from the main-body-side movable magnet 5 and returns to the original position. Therefore, by setting the time constant to a small value as described above, the followability of the main body-side movable magnet is improved, and the main body-side movable magnet 5 is made to reliably follow the position of the vibration center of the rod-side magnet 9. ing.
[0032]
Similarly, when it is determined in S3 that the vertical G of the vehicle body is equal to or greater than the predetermined value, the load applied to the mount increases due to the inertial force of the vehicle body and the engine, and the process proceeds to S6. If the throttle is turned on when the vehicle is stopped in S4, the process proceeds to S6 because the engine torque greatly fluctuates and the load acting on the magnetic spring mounting device increases. Further, when it is determined in S5 that the vehicle is accelerating or decelerating, for example, when the accelerator is opened, when the engine speed increases during downshifting, when the accelerator is closed, etc., it is caused by the torque reaction of the engine. As a result, the load acting on the magnetic spring mounting device increases, and the process proceeds to S6.
After setting the time constants T1 and T2 in S6 or S7, the process proceeds to S8, in which the displacement X input in S1 is multiplied by a predetermined coefficient K, and the value of the time constant T1 or T2 that has passed through the low-pass filter is used as the main body side. The target displacement Tr of the movable magnet 5 is calculated. Next, proceeding to S9, the main body side movable magnet 5 is moved by the target displacement Tr by feedback control.
[0033]
As described above, in a vehicle operating state in which the load acting on the magnetic spring mounting device is considered to increase, the followability of the main body side movable magnet 5 to the rod side magnet 9 is always increased, so that the configuration shown in FIGS. As shown in FIG. 5, the range (A, A ′) in which the spring constant of the entire device (see the solid line {circle around (3)} in FIGS. 2 and 5) is 0 can be moved in accordance with the vibration position. As a result, it is possible to prevent the vibration of the engine and the suspension from being largely transmitted to the vehicle body and increase the vibration noise that the occupant feels uncomfortable. Since the body-side movable magnet 5 and the rod-side magnet 9 are always located close to each other, a relatively small motor is used for driving the body-side movable magnet, since it is only necessary to correct a minute relative displacement. And power consumption for control is reduced.
[0034]
The above-described embodiment is an example in which the magnetic spring mount device is applied to an engine mount, but can be applied to other uses. When applied to a suspension mount, a suspension is mounted on the support plate 7 described above, and the main body case 3 is mounted on the vehicle side. Conversely, a suspension may be attached to the main body case 3 and the support plate 7 may be attached to the vehicle. In the case of this suspension mount, the load acting on the magnetic spring mount device from the suspension side increases when traveling on a road with large undulations, during acceleration / deceleration, and when traveling on a curve. Similarly to the case where the present invention is applied as an engine mount, it is possible to prevent the vibration of the suspension from being transmitted to the vehicle. As a result, the suspension vibration is insulated even when the vehicle is running, such as when traveling on a highly uneven road surface, during acceleration / deceleration, or when traveling on a curve, and the vibration noise that the occupant feels uncomfortable is reduced favorably.
[0035]
Furthermore, when applied to a suspension mount, the static load acting on the magnetic spring mount device from the vehicle side changes depending on the number of occupants and the amount of cargo loaded, and the vibration input range may deviate from the range of A in FIG. As shown in FIG. 5, by moving the range where the spring constant of the entire apparatus becomes 0 as indicated by A ′, even when vibration noise is generated due to the change in the static load, the occupant is similarly moved. Can reduce vibration noise that is uncomfortable.
[0036]
Further, the magnetic spring mounting device according to the present embodiment can be applied to a cab (cabin) mount of a truck or a construction machine. In the case of a cab mount, the above-described support plate 7 is attached to a vehicle except for the cab, and the main body case 3 is attached to the cab. Alternatively, conversely, the main body case 3 may be attached to a vehicle except for the cab, and the support plate 7 may be attached to the cab. In the case of this cab mount, as in the case of the above-described engine mount and suspension mount, the vibration transmitted from the vehicle body side to the cab during driving on a rough road surface, acceleration / deceleration, curve running, etc. is good. (Insulation).
Also, in the cab mount, similarly to the suspension mount, since the weight (static load) of the entire cab varies depending on the number of occupants, the vibration input range may deviate from the range of A in FIG. However, in such a case, as shown in FIG. 5, by moving the range where the spring constant of the entire apparatus becomes 0 as A ', and by changing the static load, the vibration noise In the case where occupancy occurs, the vibration noise that the occupant feels uncomfortable can be similarly reduced.
[0037]
Next, even when the following control is performed by moving the movable magnet 5 by the drive motor 22, the output characteristics of the drive motor 22, the set values of the time constants T1 and T2, the sizes of the magnets 5 and 9, Due to a gap or the like, there is a limit of the relative displacement between the magnets 5 and 9 that the main body side movable magnet 5 can follow, that is, an allowable range. Therefore, when a large vibration input exceeding the allowable range is applied, the magnets 5 and 9 are balanced at the positions as shown in FIG. Position before joining). When the magnetic spring mount device of the present embodiment is applied to an engine mount or the like of an automobile, it is necessary to use a magnet having a strong magnetic force as described above, and a large force is required to return the magnet to its original position. . Therefore, in such a case, if the drive motor 22 attempts to return the magnets 5 and 9 to their original positions, a drive motor having a large output is required. However, since such a motor is large, the mounting space is restricted. However, it is not preferable for practical use because it causes high cost, increases power consumption, and the like. Thus, in the present embodiment, this problem is solved as follows.
[0038]
In the present embodiment, the control shown in the flowchart of FIG. 7 is performed to solve this problem. The lock control of the movable magnet 5 according to the present embodiment will be described below with reference to FIG. In FIG. 7, S indicates each step.
First, in S11, it is determined whether or not the axial distance between the main body side movable magnet 5 and the rod side magnet 9 is within an allowable value. Here, the allowable value is the maximum value of the distance between the main body side movable magnet 5 and the rod side magnet 9 that allows the main body side movable magnet 5 to follow the rod side magnet 9 by the control shown in FIG. This allowable value is determined by the output of the drive motor, the values of the time constants T1 and T2, the sizes and gaps of the magnets 5 and 9, and the like. In S11, when it is determined that the distance between the main body side movable magnet 5 and the rod side magnet 9 is equal to or less than the allowable value, the process proceeds to S12, where it is determined whether the flag F is 1 or not. Proceeds to S13, and performs the control shown in FIG. Here, F = 1 means that the movable magnet 5 described later is in a locked state (see S16).
[0039]
In S11, when it is determined that the distance between the main body side movable magnet 5 and the rod side magnet 9 is larger than the allowable value, the process proceeds to S14. In S14, the control of FIG. 6 is performed in a state where the distance between the movable magnet 5 and the magnet 9 is maintained. Further, instead of the control of FIG. 6, a control similar to the control of FIG. 6 in which the followability of the main body side movable magnet 5 to the rod side magnet 9 is considerably reduced may be performed. In the latter case, the time constant T is set to a value larger than the time constant T2. Further, in S14, a warning (alarm) to that effect is issued to the driver.
[0040]
Next, in S15, for example, it is determined whether the vehicle is starting or the engine is starting. The point is that it is not necessary to start the vehicle or start the engine, and it is sufficient to determine whether or not the vehicle is in an operating state in which a very large load is applied. In such a case, a very large load is applied to the magnetic spring mounting device, and the magnet 9 is displaced by this load, so that the distance between the movable magnet 5 and the magnet 9 falls within the normal controllable allowable value shown in FIG. There are cases. Therefore, in the case of YES in S15, the process proceeds to S16, where the main body side movable magnet 5 is locked at the current position, and the rod side magnet 9 returns to the locked position of the main body side movable magnet 5 or a position near the locked position. wait. The lock position of the main body side movable magnet 5 may be an initial static balance position.
The main body side movable magnet 5 can be locked by an electromagnetic lock (electric lock) of the motor. When the position cannot be completely locked by the electromagnetic lock alone and the position is moved by a magnetic force, the lock is mechanically performed by the lock mechanism 29 or by providing a brake device (not shown) on the motor output shaft. May be.
[0041]
Next, the flag F is set to 1 in S17. In the case of NO in S15, it is considered that a large vibration input is not applied to the magnetic spring mounting device, and thus such lock control is not performed.
Next, returning to S11, if it is determined that the value is within the allowable value, the process proceeds to S12, and since F = 1 (in a locked state), the process proceeds to S18 to lock the main body-side movable magnet 5. Is released, and the flag F is set to 0 in S19.
[0042]
By the lock control as described above, even when the distance between the main body side movable magnet 5 and the rod side magnet 9 exceeds the allowable value and the normal control (following control) shown in FIG. By utilizing a large vibration input of the vehicle or the engine, the distance between the main body side movable magnet 5 and the rod side magnet 9 can be easily returned to the normally controllable distance shown in FIG.
[0043]
In the lock control shown in FIG. 7, the follow-up control is performed in S14. However, without performing the follow-up control, a warning (alarm) is issued or without a warning (alarm), and the main body side movable magnet is not issued. 5 may be locked in the current position or the initial static balance position.
[0044]
【The invention's effect】
According to the present invention, vibration can be effectively insulated even when a large load is applied to the magnetic spring mounting device.
[Brief description of the drawings]
FIG. 1 is a structural view showing a magnetic spring mounting device on which the embodiment of the present invention is based.
FIG. 2 is a load-displacement characteristic diagram of the magnetic spring mounting device of FIG. 1 and the magnetic spring mounting device in the state of FIG.
FIG. 3 is an overall configuration diagram showing an embodiment of a magnetic spring mounting device of the present invention.
FIG. 4 is a structural view showing the magnetic spring mounting device of FIG. 3;
FIG. 5 is a load-displacement characteristic diagram of the magnetic spring mounting device in the state of FIG. 4 (b).
FIG. 6 is a flowchart for following control of the main body side movable magnet according to the present embodiment.
FIG. 7 is a lock control flowchart of the main body side movable magnet according to the present embodiment.
[Explanation of symbols]
1 Magnetic spring mounting device
2 vehicles
3 Body case
5 Moving magnet (first magnet)
7 Support plate
8 rod
9 magnet (second magnet)
10 Spring
12,13 Displacement sensor
20 Interface
21 CPU
22 Drive motor
23 Driver for drive motor
24 Steering angle sensor
25 Vertical G sensor
26 Accelerator sensor
27 Brake sensor
28 Vehicle speed sensor
29 Lock mechanism

Claims (6)

A magnetic spring mount device that supports a heavy object by a combined force of a force of a spring and a force of a magnet,
A first member to which an axially movable first magnet is attached;
A second member disposed so as to be capable of reciprocating relative to the first member via a spring member and having a second magnet attached to a position corresponding to the first magnet;
Magnet driving means for moving the first magnet of the first member along the axial direction;
A heavy object to be supported is attached to the first member or the second member. The first magnet of the first member is moved by the magnet driving means, and the force of the spring member and the force of the first magnet and the second magnet are applied. Control means for ensuring that the resultant force is always substantially constant in a predetermined displacement range of the second member;
When the distance between the first magnet and the second magnet in the axial direction is larger than a predetermined allowable value, the first magnet is locked. When the distance becomes smaller than the predetermined allowable value, the locking of the first magnet is performed. Magnet lock means for releasing
A magnetic spring mounting device comprising: 2. The magnetic spring mounting device according to claim 1, wherein said magnet lock means electrically locks said magnet drive means. 2. The magnetic spring mounting device according to claim 1, wherein said magnet locking means mechanically locks said magnet driving means. 4. The magnetic spring mounting device according to claim 1, wherein said magnet locking means locks said first magnet at a predetermined position. 5. The magnetic mount device according to claim 1, wherein the magnet lock unit locks the first magnet when a predetermined large load acts on the first member or the second member. 6. The magnetic mounting device according to claim 1, further comprising an alarm unit that issues an alarm when the first magnet is locked by the magnet lock unit.

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