JP4539461B2 - Eddy current reducer - Google Patents

Description

The present invention relates to an eddy current speed reducer, and more particularly to an improvement of an eddy current speed reducer having a structure in which a permanent magnet is moved closer to and away from a brake disk connected to a rotating shaft.

  There are several types of eddy current type speed reducers used for auxiliary brakes of large vehicles such as trucks. Focusing on the shape of the braking member connected to the rotating shaft, it is roughly divided into a type that employs a disc-shaped braking member (disc type) and a type that employs a drum-shaped braking member. A disc-type braking device employs a structure in which a permanent magnet is slid along a rotating shaft, and the magnet is moved toward and away from a braking disc connected to the rotating shaft.

  As a disk-type eddy current reduction device, for example, as disclosed in Japanese Patent Application Laid-Open No. 2004-48978, a permanent magnet is fixed to a magnet holding member connected to a drive unit such as an actuator. A plurality of actuators are arranged along the outer periphery of the disk-shaped magnet holding member, and each actuator is operated in synchronization. Thereby, the magnet holding member and the braking surface of the braking disk are always maintained in a parallel state.

JP 2004-48978 A

  By the way, in the disc type speed reducer, an attractive force acts between the brake disc and the magnet during braking. In order to switch to the non-braking state, it is necessary to pull the magnet away in the direction opposite to this attractive force. For this reason, the actuator used for the movement of the magnet holding member requires a force larger than the magnet attractive force.

  Therefore, as disclosed in Japanese Patent Application Laid-Open Nos. 2003-319637 and 2004-72972, methods have been proposed in which the magnet holding member is tilted away from the brake disk to reduce the capacity of the actuator. In these reduction gears, the magnet holding member and the actuator are connected by a so-called “pin support structure” including a shaft and a bearing.

JP 2003-319637 A JP 2004-72972 A

  However, as disclosed in Japanese Patent Application Laid-Open No. 2004-48978, in a device in which the magnet holding member and the braking surface of the braking disk are always in parallel, it is difficult to operate a plurality of actuators in complete synchronization. Therefore, there is a possibility that the operation position may not be aligned and the magnet holding member may malfunction during movement. Further, since the joint portion between the actuator and the magnet holding member is supported rigidly, there is a possibility that high stress concentrates on the base portion.

  On the other hand, as disclosed in Japanese Patent Application Laid-Open No. 2003-319637 and Japanese Patent Application Laid-Open No. 2004-72972, in a device that can move the magnet holding member in an inclined state, a pin support structure is adopted, so that the dimensional accuracy and use of parts There is a possibility of looseness at the connecting part due to wear inside. If play occurs in the pin support portion, the magnet holding member cannot be held at the original braking position and good braking characteristics cannot be exhibited. Further, there is a possibility that the magnet holding member may vibrate due to vibration from the vehicle. Further, the structure of the shaft portion and the bearing portion is complicated, and there is a problem that the number of parts increases.

In view of these problems, an object of the present invention is to provide an eddy current type speed reducer that has a simple configuration and can be switched between good braking and non-braking. In particular, in an apparatus of a type in which the magnet holding member is driven in parallel to the brake disk, an object is to alleviate the stress concentration at the joint portion between the actuator and the magnet holding member. Another object of the present invention is to improve the durability of an apparatus of the type that moves the magnet holding member in an inclined state with respect to the brake disk and suppresses rattling at the joint between the actuator and the magnet holding member.

  In order to achieve the above object, an eddy current reduction device according to a first aspect of the present invention includes a braking disk coupled to a rotating shaft of a vehicle; a permanent disk disposed opposite to the braking surface of the braking disk. A magnet; a magnet holding means connected to the non-rotating portion of the vehicle and holding the permanent magnet; and a driving means for driving the magnet holding means along the rotating shaft so as to approach and separate from the braking disk. And a connecting member for connecting the driving means and the magnet holding means. And the said connection member is shape | molded with an elastic material.

  Here, the “elastic material” is a material that uses elastic deformation, and is usually used for vibration control, application of restoring force, repetitive operation, and the like. Piano wire, spring steel, phosphor bronze, Co-based alloy Ni base alloy, Elinvar alloy, etc. are generally called spring materials. Among them, a material having a certain degree of rigidity and capable of elastic deformation within a predetermined range is preferable. Typical examples are spring steels having an elastic constant of 190 to 210 GPa, such as JIS G4801 (spring steel material), JIS G4802 (cold rolled steel strip for springs), JIS G3560 (oil tempered wire for springs), A material selected from JIS G4313 (stainless steel strip for spring), JIS G4314 (stainless steel wire for spring), and the like can be used. SK5-CSP (with an elastic constant of about 206 GPa) can also be used.

  The “rotating shaft” is not limited to the one connected to the engine, and any rotating shaft of the “vehicle” can be installed. For example, it can be installed on a wheel shaft that is not a moving wheel. “Vehicle” is a concept that includes railway vehicles in addition to automobiles. The “non-rotating portion of the vehicle” refers to a portion that is relatively fixed in the vehicle, for example, a chassis, a body, a railcar, etc. of an automobile.

  The permanent magnet may be composed of a plurality of permanent magnets arranged such that the magnetic pole surface faces the braking surface of the braking disk and adjacent magnetic poles are different.

  When the magnet holding means is structured to move so that the magnetic pole surface of the permanent magnet is always substantially parallel to the braking disk, stress concentration at the joint between the actuator and the magnet holding member can be reduced. This contributes to improving the durability of the device.

  On the other hand, when the magnet holding means is configured to be tiltable with respect to the brake disk, it is possible to suppress the play at the joint portion between the actuator and the magnet holding member and to improve the durability. Further, the number of parts can be greatly reduced as compared with the conventional pin support structure. Furthermore, by applying a moment due to the elastic deformation of the connecting member to the magnet holding member, it is possible to reduce the size of the device and employ a braking disk made of a nonmagnetic material.

  When the magnet holding means is structured to be tiltable with respect to the brake disk, the connecting member can be structured to connect the driving means and the magnet holding means at a single location.

  Further, when the brake disk is formed of a ferromagnetic material, the magnet holding means is kept substantially parallel to the brake disk in the non-braking state and the braking state, and the brake state is changed to the non-braking state. It is preferable that the magnet holding means is inclined with respect to the brake disk and the connecting member is elastically deformed when switching. In this case, it is possible to further include an auxiliary spring that urges the magnet holding means in a direction away from the braking disk when the braking state is switched to the non-braking state. When the brake disk is made of a ferromagnetic material, it contributes to reducing the size and weight of the device.

  On the other hand, when the brake disk is formed of a non-magnetic material, the magnet holding means is inclined with respect to the brake disk in the non-braking state, and in the braking state, the connecting member is elastically deformed and the brake disk is deformed. It is preferable that the magnet holding means is configured to be parallel to the braking surface of the braking disk against the force. When the brake disk is made of a non-magnetic material, the magnet holding member is stably held at the original brake position, thereby preventing performance degradation and exhibiting stable performance.

  In the present invention, by appropriately changing the configuration of the elastic support member (connection member) in accordance with the magnetization characteristics of the disk, it is possible to further reduce the size of the device and prevent performance degradation during braking.

  In the apparatus of the present invention, a guide member that is supported by a non-rotating portion includes a restricting member that restricts the position of the magnet holding means on the braking disk side, and a cushion member that the magnet holding member abuts in a non-braking state. It is preferable to provide the tube.

The driving means may be an actuator, and the connecting member may be fixed to a rod tip of the actuator. The connecting member may be formed in a rod shape, threaded on the outer periphery of one end, and screwed into the rod tip to be fixed. At this time, it is preferable that the other end of the connecting member is fixed to the magnet holding means in a state bent toward the center direction of the rotation shaft. Alternatively, the connecting member may be formed in a plate shape and fixed to the rod tip and the magnet holding means by bolting.

  Hereinafter, the best mode for carrying out the present invention will be described in detail using embodiments.

  FIG. 1 and FIG. 2 are cross-sectional views showing the structure of the main part of an eddy current type speed reducer (retarder) 10 according to a first embodiment of the present invention, and show a non-braking state and a braking state, respectively. The eddy current type speed reducer 10 according to the present embodiment includes a braking disk 14 made of a ferromagnetic material connected and fixed to a rotating shaft 12 of an engine; and a braking surface (left surface in the figure) of the braking disk 14. A permanent magnet 16 disposed; a magnet holding member 18 that is fixed to a non-rotating part such as a vehicle chassis and holds the permanent magnet 16; and a rotating shaft so that the magnet holding member 18 approaches and separates from the brake disk 14 12, an actuator 20 serving as a driving unit that is driven along 12; and a connecting member 24 that connects the actuator 20 and the magnet holding member 18.

  The rotating shaft 12 is connected to a propeller shaft of a large vehicle (truck), for example. The actuator 20 has an air cylinder, a piston, and an actuator rod 22 connected to the connecting member 24.

  The connecting member 24 is formed of an elastic material having a certain degree of rigidity and capable of elastic deformation within a predetermined range. Specifically, a material having an elastic constant of about 190 GPa to 210 GPa can be used. For example, JIS G4801 (spring steel material), JIS G4802 (cold rolled steel strip for springs), JIS G3560 (oil tempered wire for springs), JIS G4313 (stainless steel strip for springs), JIS G4314 (stainless steel wire for springs) ) Etc. can be used. SK5-CSP (with an elastic constant of about 206 GPa) can also be used. The specific structure of the connecting member 24 will be described later.

  One end of the connecting member (elastic support member) 24 is fixed to the tip of the actuator rod 22, and the other end is fixed to the magnet holding member 18. The connecting member 24 is preferably a plate-like spring or a rod-like spring, and a material that can be used in the elastic region is selected within a range in which the magnet holding member 18 tilts. The fixing method of the connection member 24 can be determined according to materials and structures, such as bolt fastening, welding, and a rivet. As the magnet holding member 18 is tilted, the connecting member 24 is elastically deformed, and the apparatus is configured such that a bending moment due to the elastic deformation acts on the magnet holding member 18. Since the connecting member 24 is firmly fixed to the magnet holding member 18 and the actuator rod 22 by bolt fastening or the like, there is no backlash of the support portion unlike the conventional pin support structure. One connecting member 24 can be used for one actuator 22, and the number of parts is small and the structure is simple compared to the structure of the shaft and the bearing of the pin support structure.

  For example, the permanent magnet 16 is disposed so as to face the surface (braking surface) of the braking disk 14 in the circumferential direction of the magnet holding member 26. The permanent magnet 16 is composed of a plurality of permanent magnet pieces, and the permanent magnet pieces are arranged such that adjacent magnetic pole faces are opposite to each other. As shown in FIG. 1, the permanent magnet 16 moves away from the braking disk 14 and enters the non-braking state, and as shown in FIG. 2, the permanent magnet 16 approaches the surface of the braking disk 14 and enters the braking state. That is, a braking torque is generated by applying a magnetic force from the permanent magnet 16 to the braking surface of the rotating braking disk 14.

  FIG. 3 is a plan view showing the configuration of the stator of the retarder 10 according to the first embodiment, and shows a state where the cover is removed for convenience. As shown in the figure, one actuator 20 is arranged on the upper part of the guide cylinder 32 fixed by the bolt 34, and has a structure in which a force is applied to the upper end of the magnet holding member 18. As a result, the magnet holding member 18 can slide while being inclined with respect to the braking surface of the braking disk 14. Three stoppers 26 a to 26 c are provided on the outer periphery of the guide cylinder 32. Of these, the stopper 26b is disposed on the opposite side (180 ° position) of the actuator 20, and the other stoppers 26a and 26c are disposed at positions shifted 90 degrees clockwise and counterclockwise from the actuator 20. Each stopper 26a-26c is shape | molded in the square pillar shape whose cross section is substantially square, and the edge part by the side of the magnet holding member 18 is shape | molded by the hook. This hook-like portion is caught by the outer edge portion of the magnet holding member 18 and is prevented from excessively approaching the brake disk 14.

  In addition to the stoppers 26a to 26c described above, a cushion 28 is provided on the surface of the guide cylinder 32 on the brake disk 14 side. The cushion 28 is formed in a cylindrical shape, and the back surface of the magnet holding member 18 abuts in a non-braking state. In the present embodiment, since the magnet attractive force and the braking reaction force do not act at the non-braking position, basically it is not necessary to elastically deform the connecting member 24. However, in order to prevent the magnet holding member 18 from being vibrated due to vibration or the like, the connecting member 24 is slightly elastically deformed so that the magnet holding member 18 is pressed against at least one cushion 28 disposed in the guide tube 32. I am letting.

  4 and 5 are sectional views showing the operation (action) of the retarder 10 according to the present embodiment, and show a braking state (FIG. 4) and a state in the middle of switching from the braking state to the non-braking state (FIG. 5). . FIG. 6 is a graph showing the action (magnetic characteristics) of the retarder 10 according to the present embodiment, and shows the relationship between the tilt angle of the magnet holding member 18 and the moment. As the magnet holding member 18 is tilted, the connecting member 24 is elastically deformed, and a bending moment due to the elastic deformation acts on the magnet holding member 18. As shown in FIG. 6, the moment due to the magnet attractive force of the magnet holding member 18 is the largest when the magnet holding member 18 is directly facing the braking disk 14 (tilt angle 0), and decreases as the tilt angle increases. To do.

  In the conventional pin support structure, when switching from the braking state to the non-braking state, it is necessary to incline the magnet holding member until the moment of the magnet attractive force becomes sufficiently small, and the same structure as the apparatus shown in FIGS. In the case, it was necessary to incline to about 3 °. According to the present embodiment, the connecting member 24 is not elastically deformed and has a bending moment of 0 when facing the braking disk 14. When the magnet holding member 18 tilts when switching from the braking state to the non-braking state, the bending by the connecting member 24 is performed in the direction opposite to the moment due to the magnet attractive force, that is, the direction in which the magnet holding member 18 is pulled away from the braking disk 14. The moment acts according to the tilt angle.

  As shown in FIG. 6, the bending moment due to the connecting member 24 increases in proportion to the increase in the inclination angle of the magnet holding member 18. When the magnet holding member 18 is tilted to a position where the bending moment of the connecting member 24 becomes large with respect to the moment of the magnet attractive force (the direction of the moment is reverse), the magnet holding member 18 is It is pulled away from the braking disk 14 and moves to the non-braking position (see FIG. 1). Compared to the conventional technology that uses a pin support mechanism to connect the magnet holding member and the actuator, the magnet tilt angle can be remarkably reduced. As a result, the size of the device in the direction of the rotation axis can be reduced, and the device can be made lighter Contributes to

  FIG. 7 is a cross-sectional view showing the structure of the main part of the retarder 110 according to the second embodiment of the present invention, and shows a non-braking state. FIG. 8 is a cross-sectional view showing the structure of the main part of the retarder 110 according to the second embodiment, showing a braking state. FIG. 9 is a graph showing the action (magnetic characteristics) of the retarder 110 according to the second embodiment, and shows the relationship between the tilt angle of the magnet holding member and the moment. In the present embodiment, the same or corresponding components as those in the first embodiment described above are denoted by the same reference numerals, and redundant description is omitted. In this embodiment, an auxiliary spring 40 is added to the first embodiment described above.

  The auxiliary spring 40 has a structure that applies force to the magnet holding means 18 in a direction away from the brake disk 14 when switching from the braking state to the non-braking state. The auxiliary spring 40 is formed in a U-shape that is open at the top, and one end is fixed to the guide tube 32 by a bolt 44. The other end has a structure in contact with the contact plate 42 provided at the lower end of the outer periphery of the magnet holding member 18 in the braking state.

  As shown in FIG. 9, also in this embodiment, the moment due to the magnet attractive force of the magnet holding member 18 is greatest when the magnet holding member 18 is directly facing the braking disk 14 (tilt angle 0). It decreases as the tilt angle increases. However, in the present embodiment, when the device 110 is switched from the braking state to the non-braking state, the force of the auxiliary spring 40 acts on the magnet holding member 18, and the bending moment of the connecting member 24 increases accordingly. That is, according to the present embodiment, an increase in moment due to the auxiliary spring 40 is generated, so that the inclination angle of the magnet holding member 18 can be further reduced as compared with the first embodiment, as shown in FIG. . As a result, it is possible to reduce the dimensions of the guide cylinder 32 and the actuator 20 in the direction of the rotation axis, thereby further reducing the mounting space of the apparatus.

  10 and 11 are sectional views showing the structure of the main part of the retarder 210 according to the third embodiment of the present invention, and show a non-braking state (FIG. 10) and a braking state (FIG. 11). In the present embodiment, the same or corresponding components as those in the first and second embodiments described above are denoted by the same reference numerals, and redundant description is omitted. The apparatus 210 according to the present embodiment has a structure in which a cover 50 that covers the magnet holding member 18 is added to the apparatus 10 according to the first embodiment described above.

  The cover 50 is disposed between the permanent magnet 16 and the brake disk 14 and has a function of protecting the magnet 16 from heat and water from the brake disk 14. When the cover 50 is made of a material other than a non-magnetic material, the magnet holding member 18 is attracted to the cover 50, so that the attractive force and braking reaction force acting on the magnet holding member 18 are both the braking disk 14 and the cover 50. Affected by. In this case, in consideration of the suction force and / or repulsive force of the brake disk 14 and the suction force of the cover 50, the elastic reaction force characteristics corresponding to the connection member 24 are determined. The material of the cover 50 is configured by combining one or a plurality of materials such as aluminum alloy, copper alloy, stainless steel, and steel, for example, and is set so as to have appropriate magnetization characteristics according to the purpose of the apparatus.

  12 and 13 are cross-sectional views showing the structure of the main part of the retarder 310 according to the fourth embodiment of the present invention, and show a non-braking state (FIG. 12) and a braking state (FIG. 13). In the present embodiment, the same or corresponding components as those in the first to third embodiments described above are denoted by the same reference numerals, and redundant description is omitted. The major difference between this embodiment and each of the embodiments described above is that the brake disk 314 is formed of a nonmagnetic material. Accordingly, the basic posture (deformed state) of the connecting member 324 made of an elastic material is different from the above-described embodiments.

  Since the brake disk 314 is made of a non-magnetic material, a repulsive force (braking reaction force) that pushes the magnet holding member 18 toward the non-braking position is applied during braking. In the conventional pin support structure, it is difficult to hold the magnet holding member at the original braking position because the magnet holding member at a position away from the actuator operating position moves backward to the non-braking position side by the braking reaction force. In this embodiment, the magnet holding member 18 is supported by the connecting member 324, and as shown in FIG. 12, the connecting member 324 is not elastically deformed at the non-braking position, and the magnet holding member 18 is inclined with respect to the brake disk 314. It is configured. On the other hand, at the braking position, the connecting member 324 is elastically deformed so that a bending moment larger than the braking reaction force and acting in the opposite direction acts on the magnet holding member 18. With such a configuration, even when the nonmagnetic disk 314 is used, the magnet holding member 18 can be held at the original braking position without being pushed back to the nonbraking position side by the braking reaction force during braking. It becomes.

  In the above embodiment, the case where a ferromagnetic material or a non-magnetic material is adopted as the material of the brake disk has been described. However, the material having intermediate magnetization characteristics between the ferromagnetic material and the non-magnetic material, and the magnetization characteristics are different. A combination of a plurality of materials is also possible. In this case, as shown in FIG. 15, the suction force by the disk acts at the time of low rotation, but the repulsion force by the braking reaction force may act at the time of high rotation. In such a case, the elastic reaction force characteristic of the connecting member (elastic support member) is determined based on the technical idea of the first to third embodiments and the fourth embodiment so as to match the magnetization characteristics of the disk. Is preferred. Specifically, the coupling member is appropriately elastically deformed at the braking position so that a bending moment is generated so as to resist a repulsive force during high rotation during braking. Further, since the magnet attracting force is generated at the time of switching to the non-braking position at the time of low rotation, the elastic reaction force characteristic of the connecting member is determined so that the bending moment due to the elastic deformation of the connecting member becomes larger than the magnet attracting force. .

  Needless to say, the direction of the bending moment due to the elastic deformation during braking and the direction of the bending moment due to the elastic deformation generated when switching to the non-braking position are opposite to each other. Examples of materials having intermediate magnetic properties used for brake disks include martensitic stainless steel, duplex stainless steel, cold-worked austenitic stainless steel, and high alloy heat resistant steel. In addition, when a braking disk is composed of a plurality of materials having different magnetization characteristics, ferritic stainless steel, steel, cast iron, etc., which are ferromagnetic materials, are used for materials such as austenitic stainless steel, aluminum alloy, and copper alloy that are nonmagnetic materials. It can be constituted by a method such as plating, clad or cast-in.

  16 to 18 are a plan view (A) and a sectional view (B) showing the structure of an elastic connecting member applicable to the present invention. The connecting members 424, 524, and 624 shown in FIGS. 16 to 18 are applicable to the connecting members (24 and 324) of the first to fourth embodiments described above. A connecting member 424 shown in FIG. 16 has a structure in which one end of a rod-shaped elastic member (spring) having a circular cross section is threaded and screwed into a hole formed in the actuator rod 22 to be fixed. The other end of the connecting member 424 is bent into an L shape and fixed to the magnet holding member 18 by welding.

  If the connecting member itself is of high strength and difficult to thread or is not suitable for welding, as shown in FIG. 17, one end of a plate-like elastic member (spring) 524 is magnet-held by a bolt 528. The other end is fixed to the support member pressing plate 530 with a bolt 528. Then, the support member pressing plate 530 is fixed to the actuator rod 22 by the bolt 526. Alternatively, as shown in FIG. 18, the other end on the actuator side of the connecting member 624 can be bent in an L shape without using the support member pressing plate (530), and can be directly fixed to the actuator rod 22 by the bolt 626. .

In each of the embodiments described above, the type of device in which the magnet holding member 18 is tilted and slid (tilted) has been described. Needless to say, the present invention can also be applied to a type of apparatus that moves so that the magnetic pole surface is always substantially parallel to the brake disk 14. In this case, the stress concentration at the joint between the actuator and the magnet holding member can be relaxed, and there are various merits such as contributing to the improvement of the durability of the apparatus. Further, as a mechanism for driving the magnet holding member, a mechanism other than the actuator may be employed, and may be manually operated when the operating force is small. In the case of an actuator, it may be a cylinder that is operated by air or hydraulic pressure, or may be an actuator by an electric motor or solenoid.

FIG. 1 is a cross-sectional view showing the structure of the main part of a retarder according to a first embodiment of the present invention, showing a non-braking state. FIG. 2 is a cross-sectional view showing the structure of the main part of the retarder according to the first embodiment, showing a braking state. FIG. 3 is a plan view showing the configuration of the stator of the retarder according to the first embodiment, and shows a state where the cover is removed for convenience. FIG. 4 is a cross-sectional view showing the operation (action) of the retarder according to the first embodiment, showing a braking state. FIG. 5 is a cross-sectional view showing the operation (action) of the retarder according to the first embodiment, showing a state in the middle of switching from the braking state to the non-braking state. FIG. 6 is a graph showing the action of the retarder according to the first embodiment, and shows the relationship between the inclination angle of the magnet holding member and the moment. FIG. 7 is a cross-sectional view showing the structure of the main part of the retarder according to the second embodiment of the present invention, and shows a non-braking state. FIG. 8 is a cross-sectional view showing the structure of the main part of the retarder according to the second embodiment, showing a braking state. FIG. 9 is a graph showing the action of the retarder according to the second embodiment, and shows the relationship between the inclination angle of the magnet holding member and the moment. FIG. 10 is a cross-sectional view showing the structure of the main part of the retarder according to the third embodiment of the present invention, and shows a non-braking state. FIG. 11 is a cross-sectional view showing the structure of the main part of the retarder according to the third embodiment, showing a braking state. FIG. 12 is a sectional view showing the structure of the main part of the retarder according to the fourth embodiment of the present invention, and shows a non-braking state. FIG. 13: is sectional drawing which shows the structure of the principal part of the retarder based on 4th Example, and shows a braking state. FIG. 14 is a cross-sectional view showing the operation (action) of the retarder according to the fourth embodiment, and shows the force (moment) acting in the braking state. FIG. 15 is a graph showing the action of the retarder according to the fourth embodiment, and shows the relationship between the rotational speed of the braking disk (rotating shaft) and the force that the magnet holding member receives in the rotating shaft direction. FIG. 16 is a plan view (A) showing the structure of a connecting member applicable to the present invention, and a cross-sectional view (B) in the AA direction of FIG. FIG. 17 is a plan view (A) showing the structure of another connecting member applicable to the present invention, and a cross-sectional view (B) in the AA direction of FIG. FIG. 18 is a plan view (A) showing the structure of still another connecting member applicable to the present invention, and a cross-sectional view (B) in the AA direction of FIG.

Explanation of symbols

10, 110, 210, 310 Eddy current type reduction device 12 Rotating shaft 14, 314 Brake disk 16 Permanent magnet 18 Magnet holding member 20 Actuator 22 Actuator rod 24, 324 Connecting member (elastic support member)
26a, 26b, 26c Stopper 28 Cushion 32 Guide tube 40 Auxiliary spring

Claims (10)

A brake disc connected to the rotating shaft of the vehicle;
A permanent magnet disposed opposite the braking surface of the braking disk;
Magnet holding means connected to the non-rotating part of the vehicle and holding the permanent magnet;
Driving means for driving the magnet holding means along the rotating shaft so as to approach and separate the braking disk;
A connecting member for connecting the driving means and the magnet holding means;
An eddy current type speed reducer characterized in that the connecting member is formed of an elastic material.   The eddy current reduction device according to claim 1, wherein the elastic material is a spring steel material.   3. The eddy current reduction device according to claim 1, wherein the magnet holding unit moves so that a magnetic pole surface of the permanent magnet is always substantially parallel to the brake disk. 4.   3. The eddy current reduction device according to claim 1, wherein the magnet holding means is structured to be tiltable with respect to the brake disk.   The eddy current reduction device according to claim 4, wherein the connecting member connects the driving unit and the magnet holding unit at a single location.   The brake disk is formed of a ferromagnetic material, and the magnet holding means is kept substantially parallel to the brake disk in the non-braking state and the braking state, and the magnet is switched from the braking state to the non-braking state. 6. The eddy current reduction device according to claim 4, wherein the holding means is structured to be inclined with respect to the brake disk and the connecting member is elastically deformed.   The eddy current reduction device according to claim 6, further comprising an auxiliary spring that urges the magnet holding means in a direction away from the braking disk when the braking state is switched to the non-braking state. .   The braking disk is formed of a non-magnetic material, the magnet holding means is inclined with respect to the braking disk in a non-braking state, and the connecting member is elastically deformed in a braking state to counter the reaction force of the braking disk, The eddy current reduction device according to claim 4 or 5, wherein the magnet holding means is configured to maintain substantially parallel to the braking surface of the braking disk. A guide tube supported by the non-rotating part;
The eddy current type according to claim 4, 5, 6, 7 or 8, further comprising a regulating member fixed to the guide cylinder and regulating a position of the magnet holding means on the brake disk side. Reducer. A guide tube supported by the non-rotating part;
The eddy current type deceleration according to claim 4, 5, 6, 7, 8 or 9, further comprising a cushion member fixed to the guide tube and in contact with the magnet holding member in a non-braking state. apparatus.

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