WO2023040180A1 - 制动器 - Google Patents

制动器 Download PDF

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Publication number
WO2023040180A1
WO2023040180A1 PCT/CN2022/076704 CN2022076704W WO2023040180A1 WO 2023040180 A1 WO2023040180 A1 WO 2023040180A1 CN 2022076704 W CN2022076704 W CN 2022076704W WO 2023040180 A1 WO2023040180 A1 WO 2023040180A1
Authority
WO
WIPO (PCT)
Prior art keywords
yoke core
friction
armature
movable plate
friction disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2022/076704
Other languages
English (en)
French (fr)
Inventor
鲁查
吴孔建
叶逸祥
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Altra Industrial Motion Shenzhen Co Ltd
Original Assignee
Altra Industrial Motion Shenzhen Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Altra Industrial Motion Shenzhen Co Ltd filed Critical Altra Industrial Motion Shenzhen Co Ltd
Priority to JP2023568630A priority Critical patent/JP7499986B2/ja
Priority to EP22868560.8A priority patent/EP4317734A4/en
Priority to US17/889,082 priority patent/US12025194B2/en
Publication of WO2023040180A1 publication Critical patent/WO2023040180A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0031—Devices for retaining friction material debris, e.g. dust collectors or filters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/22—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for pressing members apart, e.g. for drum brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • F16D2121/22—Electric or magnetic using electromagnets for releasing a normally applied brake

Definitions

  • the present application belongs to the technical field of mechanical brakes, and in particular relates to a brake.
  • the thickness has gradually become a key parameter to measure the performance of the brakes.
  • the overall thickness of the brakes must be small, and the traditional stacked structure brakes can no longer meet the requirements.
  • Fig. 15 is a structural schematic diagram of a brake in the prior art.
  • the brake includes a yoke 91 , an armature 94 , a friction disc 96 and a tail plate 95 , which are stacked in sequence along the direction indicated by the axis X of the braked shaft.
  • the braked shaft is connected with the friction disc 96 through the shaft sleeve 97 .
  • the braked shaft can also rotate freely.
  • the tail plate 95 is connected with the yoke 91 through a threaded connection 98 and a sleeve 99 and kept relatively fixed.
  • the armature 94 can move axially, thereby changing the distance M between the tail plate 95 and the armature 94 .
  • the friction disc 96 When the distance M becomes larger, the friction disc 96 is loosened and can rotate freely; when the distance M becomes smaller, the friction disc 96 is clamped to realize braking.
  • the armature 94 moves axially through the coil 92 and the spring 93 .
  • the spring 93 pushed the armature 94 to make it close to the tail plate 95, the distance M became smaller, and the friction disc 96 was clamped;
  • the yoke 91 when the coil 92 was energized, the yoke 91 was magnetized and attracted the armature 94, so that The armature 94 overcomes the elastic force of the spring 92, moves away from the tail plate 95, the distance M becomes larger, and the friction disc 96 is released.
  • An embodiment of the present application provides a brake, which aims to reduce the thickness of the brake and improve the braking performance of the brake.
  • a brake including:
  • the yoke core has a first installation space and a second installation groove concentrically distributed sequentially from the inside to the outside, the first installation space penetrates the center of the yoke core along the axial direction of the yoke core, and the second The opening of the second installation slot faces the second axial end of the yoke core;
  • a movable plate located in the first installation space and close to the first shaft end of the yoke core, the first shaft end being the opposite end of the second shaft end;
  • a friction disc arranged in the first installation space, and located on a side of the movable plate close to the second shaft end;
  • the armature is located at the second axial end of the yoke core, the armature is connected to the movable plate through a connecting piece, the connecting piece runs through the yoke core, and is connected to the yoke core sliding fit, the armature can drive the movable plate to move along the axial direction of the yoke core;
  • the elastic member is arranged between the armature and the yoke core, and the elastic member has a pre-tightening force to keep the armature away from the yoke core.
  • a positioning groove is formed on the first axial end surface of the yoke core, the positioning groove communicates with the first installation space, and the connecting piece passes through the positioning groove;
  • the outer periphery of the movable plate is provided with a positioning block corresponding to the positioning groove, the positioning groove is used to avoid the positioning block, and the connecting piece is connected with the positioning block.
  • the connecting piece includes a guide post and two connecting parts, the guide post is passed through the yoke core, and one end of the guide post is connected to one end of the guide post through one of the connecting parts. on the movable plate, and the other end is connected to the armature through another connecting portion.
  • an annular installation area for installing the connecting piece is formed on the yoke core, and the installation area is located between the first installation space and the second installation groove; Mounting holes are also provided in the mounting area, and the mounting holes are arranged alternately with the connecting pieces.
  • the inner surface of the first installation space close to the second shaft end extends toward the axis of the yoke core, and the inner diameter of the extension is smaller than that of the friction disc. outside diameter.
  • the friction disc includes an elastic component and a plurality of friction units, and the plurality of friction units are distributed in an annular array around the axis of the yoke core and enclose to form a central space , the friction unit has a degree of freedom to approach or move away from the middle space along the radial direction of the yoke core, the elastic components are respectively connected to a plurality of friction units, and the elastic components are configured to make the friction The preload of the monocoque near the middle space.
  • the elastic assembly includes a plurality of first tension spring groups, the first tension spring groups are connected between two adjacent friction units, and the first tension spring groups include at least one first tension spring group A tension spring, and the middle space forms a shaft sleeve fitting space.
  • the elastic components include:
  • a fixed frame located in the middle space, and the inside of the fixed frame forms a space for fitting the sleeve
  • the second tension spring set is connected between the friction unit and the fixed frame, and the second tension spring set includes at least one second tension spring.
  • the elastic assembly further includes a guide post whose end is fixed to the fixed frame, the guide post extends along the radial direction of the yoke core, and the friction unit is close to the middle space
  • a guide post whose end is fixed to the fixed frame, the guide post extends along the radial direction of the yoke core, and the friction unit is close to the middle space
  • One side of the guide post is provided with a chute that is slidably fitted with the guide post.
  • a raised portion is provided on a side of the friction unit away from the middle space.
  • the movable plate, friction disc and coil are all inside the yoke core, so the overall thickness of the brake depends on the thickness of the yoke core and the thickness of the armature, that is, the sum of the thicknesses of the yoke core and the armature, and the structure is compact , the space utilization rate is high, and the thickness is much smaller than the traditional stacked structure;
  • the friction disc, movable plate and coil are all located inside the yoke core, and their thickness will not increase the overall thickness of the brake. Therefore, the thickness of the friction disc, movable plate and coil does not need to be overly compressed, and a reasonable strength can be ensured. Ensure overall rigidity, reduce the probability of creep, do not require excessive material and processing costs, and ensure appropriate coil volume and power;
  • the thickness of the friction disc can be appropriately increased, which can not only improve the overall structural strength of the friction disc, facilitate processing, but also easily ensure the perpendicularity between the middle hole and the friction surface, increase the matching length with the sleeve or shaft, and reduce the rotation process Vibration, noise and drag torque in
  • the thickness of the friction disc and movable plate will not be too thin during friction, which can reduce the sharpness of sound generated by friction and effectively reduce noise, especially suitable for high-speed or high-quiet occasions; friction disc and The movable plate is located in the first installation space. When the brake is working, they are surrounded by the yoke core and the surrounding parts, and the noise generated by the friction of the friction disc is blocked from spreading outward, further reducing the noise;
  • the friction disc is located in the first installation space. Compared with the smaller diameter of the traditional friction disc, the friction line speed is lower at the same motor speed, which reduces the wear rate and prolongs the service life; and when the diameter of the friction disc is small, Compared with the traditional one, under the same rotating speed, the outer ring speed of the friction disc with smaller diameter is smaller, and the moment of inertia is reduced, thereby reducing the throwing out of dust;
  • the friction disc is inside the yoke core, and the dust thrown out when the friction disc rotates is also inside the yoke core, which is conducive to the cleanliness of the working environment and can also prevent dust from entering between the yoke core and the armature gap between
  • the friction disc is not in direct contact with the armature, and the accuracy requirements of the armature are lower, which reduces the manufacturing cost of the armature; the armature does not need to be made of soft magnetic materials, and materials can be selected in a wider range during design, which reduces the design of the armature.
  • Cost The structure friction between the friction disc and the movable plate and the clamping friction disc with the movable plate realizes braking. The stability is good, the precision is easy to guarantee during manufacturing, and the manufacturing cost is low; the movable plate does not need to use soft magnetic materials, and the design cost is also low; high temperature and a small amount of deformation will not affect the normal operation of the movable plate. During the use of the brake, the movable plate has more features. good reliability.
  • Fig. 1 is a front structural schematic view of the brake provided by the embodiment of the present application.
  • Fig. 2 is a schematic cross-sectional structure diagram along line A-A in Fig. 1;
  • Fig. 3 is the cross-sectional structure schematic diagram along B-B line in Fig. 1;
  • Fig. 4 is a schematic diagram of the explosion structure of the brake provided by the embodiment of the present application.
  • Fig. 5 is a second schematic diagram of the exploded structure of the brake provided by the embodiment of the present application.
  • Fig. 6 is a schematic cross-sectional structure diagram of the yoke core used in the brake provided by the embodiment of the present application;
  • Fig. 7 is a three-dimensional structural schematic diagram of the friction disc used in the brake provided by the embodiment of the present application.
  • Fig. 8 is a schematic cross-sectional structure diagram of a friction disc used in the brake provided by the embodiment of the present application.
  • Fig. 9 is a schematic perspective view of the three-dimensional structure of the friction unit used in the brake provided by the embodiment of the present application.
  • Fig. 10 is a schematic diagram of the use state of the friction disc used in the brake provided by the embodiment of the present application.
  • Fig. 11 is a schematic perspective view of the three-dimensional structure of the friction disc used in the brake provided by the embodiment of the present application;
  • Fig. 12 is a schematic cross-sectional structural view of the friction disc used in the brake provided by the embodiment of the present application.
  • Fig. 13 is a schematic perspective view of the three-dimensional structure of the friction monomer used in the brake provided by the embodiment of the present application;
  • Fig. 14 is a schematic diagram of the use state of the friction disc used in the brake provided by the embodiment of the present application.
  • Fig. 15 is a schematic structural diagram of a stacked brake in the prior art.
  • 10-Yoke core 11-First installation space; 12-Second installation slot; 13-Extension; 14-Connection hole; 15-Installation hole; 16-Blind hole; 20-movable plate; 21-positioning block; 30-friction plate; 31-friction unit; -elastic assembly; 321-first extension spring; 322-second extension spring; 323-guide column; 324-fixed frame; 33-middle space; 40-coil; 50-armature; 60-elastic piece; ; 80-connecting piece; 81-connecting part; 82-guiding column.
  • the brake includes a yoke core 10, a movable plate 20, a friction disc 30, a coil 40, an armature 50, and an elastic member 60.
  • the yoke core 10 is concentrically distributed with a first installation space 11 and a second installation groove from the inside to the outside. 12.
  • the first installation space 11 passes through the center of the yoke core 10 along the axial direction of the yoke core 10, and the opening of the second installation groove 12 faces the second axial end of the yoke core 10;
  • the movable plate 20 is located at the In an installation space 11, and close to the first shaft end of the yoke core 10, the first shaft end is the opposite end of the second shaft end;
  • the friction disc 30 is located in the first installation space 11, and is located on the movable plate 20 close to the second shaft end.
  • the coil 40 is located in the second installation groove 12;
  • the armature 50 is located at the second shaft end of the yoke iron core 10, and the armature 50 is connected with the movable plate 20 by a connecting piece 80, and the connecting piece 80 penetrates the magnet.
  • yoke core 10 and slidingly fit with the yoke core 10, the armature 50 can drive the movable plate 20 to move along the axial direction of the yoke core 10;
  • the elastic member 60 is arranged between the armature 50 and the yoke core 10, and the elastic The piece 60 has a preload that keeps the armature 50 away from the yoke core 10 .
  • the axial direction of the yoke core 10 is the thickness direction of the yoke core 10 .
  • the axis of the braked shaft passes through the center of the yoke core 10 along the thickness direction of the yoke core 10 . That is to say, the centerline of the yoke core 10 passes through the thickness direction of the yoke core 10 and coincides with the axis of the braked shaft.
  • the first shaft end is the first side of the yoke core 10
  • the second shaft end is the second side of the yoke core 10.
  • the first side and the second side are distributed along the thickness direction of the yoke core 10. different sides of the .
  • the second installation slot 12 can also be called a second installation space.
  • the yoke core 10 may also be called a yoke or a housing.
  • the yoke core 10 itself has no magnetism, but when the coil 40 is energized, the yoke core 10 is magnetized to generate magnetism; when the coil 40 is not energized, the magnetism of the yoke core 10 disappears.
  • the coil 40 When the brake provided in this application is in use, the coil 40 is electrically connected to an external power source. When the coil 40 is energized, the yoke core 10 and the armature 50 generate a magnetic force that attracts each other under the excitation of the coil 40, and the magnetic force pulls the armature 50 together, and the armature 50 moves close to the first shaft end, compressing the elastic member 60, and at the same time The movable plate 20 is driven to move away from the second shaft end.
  • the friction disc 30 is released, and the end surface is no longer pressed against the friction disc 30, and at the same time, the friction disc 30 is no longer pressed against the Cooperate with the movable plate 20 to clamp the structure of the friction disc 30 to complete the release process.
  • the friction disc 30 cooperates with the shaft or bushing 70 and rotates normally; when the power is turned off, the magnetic force on the yoke core 10 and the armature 50 disappears, the elastic member 60 releases and pushes the armature 50, the armature 50 moves away from the first shaft end, and at the same time drives the movable plate 20 to move toward the second shaft end, the end surface of the movable plate 20 is pressed against the friction disc 30, and the other side of the friction disc 30 One end face is squeezed on the structure that cooperates with the movable plate 20 to clamp the friction disc 30. Due to the frictional resistance, the rotational speed of the friction disc 30 gradually decreases until it drops to 0, and the braking process is completed.
  • the movable plate 20, the friction disc 30 and the coil 40 are all in the yoke core 10, so the overall thickness of the brake depends on the thickness of the yoke core 10 and the thickness of the armature 50, that is, the yoke core 10 and the armature
  • the friction disc 30, movable plate 20 and coil 40 are all located inside the yoke core 10, and their thickness will not increase the overall thickness of the brake, so the thickness of the friction disc 30, movable plate 20 and coil 40 does not need to be excessive Compression can ensure reasonable strength, ensure overall rigidity, reduce the probability of creep, do not require excessive material and processing costs, and ensure appropriate coil 40 volume and power;
  • the thickness of the friction disc 30 can be appropriately increased, which can not only improve the overall structural strength of the friction disc 30, facilitate processing, but also easily ensure the perpendicularity between the middle hole and the friction surface, increase the matching length with the sleeve 70 or the shaft, and reduce the Vibration, noise and drag torque during small rotations;
  • the thickness of the friction plate 30 and the movable plate 20 is not too thin during friction, which reduces the sharpness of sound generated by friction and effectively reduces noise, especially suitable for high-speed or high-quiet occasions; friction
  • the disk 30 and the movable plate 20 are located in the first installation space 11. When the brake is working, they are surrounded by the yoke core 10 and the surrounding parts, and the noise generated by the friction of the friction disk 30 is blocked from spreading outward, further reducing the noise;
  • the friction disc 30 is located in the first installation space 11. Compared with the traditional friction disc 30, the diameter is smaller, and the friction linear velocity is lower at the same motor speed, which reduces the wear rate and prolongs the service life; and the friction disc 30 has a smaller diameter Compared with the traditional one, under the same rotational speed, the outer ring speed of the friction disc 30 with a smaller diameter is smaller, and the moment of inertia is reduced, thereby reducing the throwing out of dust;
  • the friction disc 30 is inside the yoke core 10, and the dust thrown out when the friction disc 30 rotates is also inside the yoke core 10, which is conducive to clean working environment and can also prevent dust from entering the yoke iron the gap between the core 10 and the armature 50;
  • the friction disc 30 is not in direct contact with the armature 50, and the accuracy requirement of the armature 50 is relatively low, which reduces the manufacturing cost of the armature 50;
  • the range of material selection reduces the design cost of the armature 50; the structure friction between the friction disc 30 and the movable plate 20 and the clamping friction disc 30 with the movable plate 20 realizes braking, and the structure of clamping the friction disc 30 with the movable plate 20 is generally It is a fixed structure, and the diameters of the friction disc 30 and the movable plate 20 are small, the stability is good during operation, the precision is easy to ensure during manufacture, and the manufacturing cost is low; the movable plate 20 does not need to use soft magnetic materials, and the design cost is also low; high temperature and A small amount of deformation will not affect the normal operation of the movable plate 20, and the movable plate 20 has better reliability during the use of the brake.
  • a specific implementation manner of the movable panel 20 may adopt the structure shown in FIG. 2 , FIG. 5 and FIG. 6 .
  • the first axial end surface of the yoke core 10 is formed with a positioning groove 17, the positioning groove 17 communicates with the first installation space 11, and the connecting piece 80 runs through the positioning groove 17; the outer periphery of the movable plate 20
  • a positioning block 21 corresponding to the positioning groove 17 is provided, the positioning groove 17 is used to avoid the positioning block 21 , and the connecting piece 80 is connected with the positioning block 21 .
  • the positioning block 21 is in the positioning groove 17, which can play the role of foolproof and facilitate installation.
  • fool-proof means that the cooperation between the positioning block 21 and the positioning groove 17 produces a restrictive effect.
  • the depth of the positioning groove 17 is greater than the thickness of the positioning block 21 .
  • One end of the connecting piece 80 is connected with the armature 50 , and the other end is connected with the positioning block 21 .
  • the design standard of the depth of the positioning groove 17 is mainly determined by the axial movement distance of the movable plate 20 .
  • Axial moving distance of the movable plate 20 length of the guide column 82 - thickness of the friction disc 30 - thickness of the extension part 13 .
  • the depth of the positioning groove 17 ⁇ the axial moving distance of the movable plate 20 + the thickness of the movable plate 20 .
  • the depth of the positioning groove 17 discussed above assumes that the movable plate 20 is always located in the first installation space 11 , that is, the movable plate 20 will not protrude from the surface of the yoke core 10 even if it moves axially.
  • the installation space of the brake is relatively loose, and even if the movable plate 20 protrudes from the surface of the yoke core 10, it will not interfere with other parts. At this time, the depth of the positioning groove 17 can be appropriately reduced, or even zero, that is, no positioning groove 17 is provided.
  • an improved implementation of the positioning groove 17 may adopt the structure shown in FIG. 5 .
  • the multiple positioning grooves 17 are evenly distributed around the axis of the yoke core 10 (ie passing through the centerline of the yoke core 10 in the thickness direction).
  • the number of positioning slots 17 is three.
  • One end of the connector 80 is connected to the positioning block 21, the number of the positioning slots 17 increases, the number of the positioning blocks 21 on the movable plate 20 will increase accordingly, and the driving force generated by the armature 50 will be more evenly delivered to the movable plate 20, and the brake Better results.
  • the positioning groove 17 shown in FIG. 5 and FIG. 6 is closer to the second installation groove 12 and the coil 40 .
  • the number of positioning grooves 17 should not be too large because the magnetic conductive material is removed from the positioning grooves 17, which may have a negative impact on the magnetic circuit. Not only the number of positioning slots 17, but also the depth of the positioning slots 17 will have a negative impact on the magnetic circuit.
  • the positioning groove 17 may no longer be an independent and separated groove as shown in FIGS. 5 and 6 , but an annular groove surrounding the middle of the yoke core 10 and coaxial with the yoke core 10 .
  • the structural form of the positioning groove 17 can be flexibly designed according to its application environment.
  • the connecting piece 80 includes a guide post 82 and two connecting parts 81 .
  • the guide post 82 is penetrated in the yoke core 10 , and one end of the guide post 82 is connected to the movable plate 20 through one connecting portion 81 ; the other end of the guide post 82 is connected to the armature 50 through the other connecting portion 81 .
  • the guide column 82 is slidingly matched with the yoke core 10 , and the two connecting parts 81 are respectively fixedly connected with the movable plate 20 and the armature 50 .
  • the axis of the guide post 82 is parallel to the axis of the yoke core 10 .
  • the guide column 82 is fixedly connected to the movable plate 20 and the armature 50 through two connecting portions 81 .
  • the implementation manner of the connecting part 81 is not limited, for example, it may be a bolt, a screw, a pin, a rivet, or the like. There is no limitation on whether the implementation manners of the two connection parts 81 are the same; that is, the two connection parts 81 may adopt the same implementation manner or different implementation manners.
  • the guide post 82 can also be fixedly connected with the movable plate 20 and the armature 50 through welding or integral molding.
  • the guide post 82 may be integrally formed with the movable plate 20; It is fixedly connected with the armature 50 by means other than forming.
  • this application does not limit the fixed connection manner of the guide column 82 with the movable plate 20 and the armature 50 . All known fixed connection methods that have not been obtained through creative labor are within the scope of protection of this application.
  • an improved implementation of the above-mentioned yoke core 10 may adopt the structures shown in FIGS. 1 to 5 . 1 to 5, the yoke core 10 is formed with an annular installation area 18 for installing the connector 80, and the installation area 18 is located between the first installation space 11 and the second installation groove 12; There are mounting holes 15, and the mounting holes 15 and the connecting pieces 80 are arranged alternately.
  • the brake When the brake is installed, the user can penetrate bolts in the mounting holes 15 and install the brake to an external object through the bolts, so that the brake can be used. Since the installation holes 15 and the connecting pieces 80 are arranged alternately, it can ensure that the brake is firmly installed, so that it has good stability during use.
  • the end surface of the first shaft end can be used as the installation flange surface.
  • the brake can be fixed to the external object through connecting parts such as bolts, pins and rivets penetrating into the installation hole 15; the end surface of the first shaft end is close to the external object.
  • the installation of the brake can also be realized at the second shaft end.
  • a boss needs to be provided at the second shaft end to reserve an axial movement space for the armature 50 .
  • the boss may be disposed on the yoke core 10 and protrude toward the outside of the yoke core 10 along the thickness direction of the yoke core 10 .
  • the protruding height of the boss is greater than the sum of the thickness of the armature 50 and the axial movement distance of the armature 50 .
  • the boss can be integrated with the yoke core 10 or can be a separate structure. In addition to being set on the yoke core 10, the boss can also be a separate part, and can also be set on an external object. The boss can be an integral structure with the external object, and can also be a split structure.
  • the connecting member 80 is connected through the connecting hole 14 on the installation area 18 .
  • the installation holes 15 and the connecting parts 80 are arranged alternately, that is, the installation holes 15 and the connection holes 14 are arranged alternately.
  • the mounting holes 15 may not be arranged alternately with the connecting holes 14 , but the alternate arrangement in this embodiment is more conducive to the stability of the brake during use.
  • the installation hole 15 may not be in the installation area 18 .
  • the mounting hole 15 may be located on the outer ring of the yoke core 10 ; or, an outwardly extending portion may be provided on the edge of the yoke core 10 , and the mounting hole 15 is disposed on the outwardly extending portion.
  • the position of the mounting hole 15 is related to factors such as the installation environment of the brake, and the technical solutions for adaptively modifying the position and structure of the mounting hole 15 according to the installation environment and other factors are all within the protection scope of the present application.
  • an improved implementation of the above-mentioned yoke core 10 may adopt the structures shown in FIGS. 1 to 6 .
  • the side of the first installation space 11 close to the second shaft end has an extension portion 13 .
  • the extension part 13 extends from the inner wall of the yoke core 10 to the center of the yoke core 10 .
  • the extension part 13 is in the shape of an annular plate, and the inner diameter of the extension part 13 is smaller than the outer diameter of the friction disc 30 .
  • the extension part 13 and the movable plate 20 are located at the two ends (ie both sides) of the friction disc 30 respectively.
  • the armature 50 drives the movable plate 20 close to the friction disc 30, and the two-axis end surfaces (ie, both sides surfaces) of the friction disc 30 rub against the movable plate 20 and the extension part 13 respectively to realize braking.
  • the extension part 13 is a specific implementation of this structure.
  • the extension part 13 can be machined integrally with the yoke core 10 with high precision; the cooperation precision between the extension part 13 and the friction disc 30 is high and the friction effect is good.
  • an improved implementation of the above-mentioned yoke core 10 may adopt the structures shown in FIGS. 3 to 4 .
  • a blind hole 16 opening toward the second shaft end is also provided in the installation area 18 .
  • the blind hole 16 is used for installing the elastic member 60 .
  • blind holes 16 are opened on both sides of each connecting hole 14 .
  • the spring namely the elastic member 60 , hereinafter referred to as spring
  • the spring can be directly arranged between the armature 50 and the yoke core 10 .
  • the selection specifications of the spring will be limited; when the blind hole 16 is set, the spring is in the blind hole 16, and the inwall of the blind hole 16 can play a certain role when the spring stretches.
  • the guiding effect, and the spring can be selected with a longer specification, and the service life is longer.
  • connection hole 14 there is a connection hole 14 between every two installation holes 15 , and a blind hole 16 is formed on both sides of the connection hole 14 , and the blind holes 16 on both sides of the connection hole 14 are also located between the two installation holes 15 .
  • the distribution of the mounting holes 15, the connecting holes 14 and the blind holes 16 may adopt other forms.
  • the distribution form of the hole structure in the installation area 18 can be flexibly designed according to the application environment.
  • a specific implementation manner of the above-mentioned friction disc 30 may adopt the structures shown in FIGS. 7 to 14 .
  • the friction disc 30 includes an elastic assembly 32 and a plurality of friction units 31, the plurality of friction units 31 are distributed in an annular array around the axis of the yoke core 10, and enclose a central space 33, the friction
  • the single body 31 has a degree of freedom to approach or move away from the middle space 33 in the radial direction of the yoke core 10.
  • the elastic components 32 are respectively connected to a plurality of friction single bodies 31, and the elastic components 32 are configured to make the friction single bodies 31 approach the middle space. 33 preload.
  • each friction unit 31 is close to each other.
  • the centrifugal force generated by the friction unit 31 overcomes the preload on the elastic component 32 force, the friction monomers 31 move along the radial direction of the yoke core 10 in a direction away from the middle space 33, two adjacent friction monomers 31 will separate from each other to form a gap, and the outer diameter of the overall friction disc 30 increases.
  • the outer arc surface of the friction element 31 abuts against the inner wall of the first installation space 11 to generate friction force to achieve the effect of braking and deceleration.
  • the friction disc 30 realizes the separation of adjacent friction units 31 at a certain speed through the split structure, thereby increasing the outer diameter of the entire friction disc 30, so that the outer arc surface of the friction unit 31 can play a braking effect, It can ensure that the brake provides additional braking function at high speed and enhances the safety of the brake.
  • the friction unit 31 can also be called a unit block.
  • the friction disc 30 is in the shape of a round pie and has a certain thickness.
  • the axis of the yoke core 10 is the center line passing through the yoke core 10 along the thickness direction of the yoke core 10 .
  • the elastic assembly 32 is respectively connected to the plurality of friction units 31 means that the elastic assembly 32 includes a plurality of elastic members, and the plurality of elastic members are respectively connected to the friction units 31 .
  • a specific implementation manner of the above-mentioned elastic component 32 may adopt a structure as shown in FIG. 8 and FIG. 10 .
  • the elastic assembly 32 includes a plurality of first tension spring groups, the first tension spring groups are connected between two adjacent friction units 31, and the first tension spring groups include at least one first tension spring 321 ,
  • the middle space 33 forms a bush fitting space.
  • Each first tension spring 321 is respectively fixed at the position between two adjacent friction monomers 31, and the two adjacent friction monomers 31 can be connected by one first tension spring 321, or by two first tension springs 321.
  • the extension springs 321 are connected (that is, one first extension spring group includes two first extension springs 321), and so on; the number of the first extension springs 321 needs to take into account the strength of the structure and the friction unit 31 when it needs to correspond to how many speeds separate.
  • the first tension spring 321 in this embodiment is not only simple in structure, but also convenient to install.
  • first tension spring 321 cannot protrude from both end surfaces of the friction unit 31 along the axial direction of the yoke core 10 , otherwise the braking effect of the two axial end surfaces of the friction disc 30 will be affected.
  • each first tension spring 321 is respectively connected to two adjacent friction units 31 .
  • a force analysis is performed on a single friction unit 31 , and its two sides are respectively subjected to the tension of the first tension spring 321 .
  • the pulling force has two components, one is a radial force directed to the center of the circle, and the other is a circumferential force perpendicular to the radial force.
  • their circumferential forces are equal in size and opposite in direction, and cancel each other out; while their radial forces are in the same direction, all pointing to the center of the circle along the radial direction, forming the friction unit 31 to The resultant force that middle space 33 moves.
  • an improved implementation of the above-mentioned friction unit 31 may adopt a structure as shown in FIGS. 8 to 9 .
  • a first accommodating groove 311 is opened on the corresponding surface of the friction monomer 31, and the corresponding surface is a side close to the adjacent friction monomer 31, and the two ends of the first tension spring 321 are respectively fixed on the two The groove bottom of the first accommodating groove 311 on the adjacent friction unit 31 .
  • the first extension spring 321 is between two adjacent friction units 31, even if the rotational speed does not exceed the preset value, the first extension spring 321 will make the adjacent friction units There is a certain gap between the bodies 31, and the length of the first extension spring 321 cannot be too long.
  • the first tension spring 321 can be in the first accommodating groove 311 when the rotation speed does not exceed the preset value, and the adjacent friction elements 31 can be attached to each other through the side, so there is It is beneficial to improve the integrity of the friction disc 30 ; and the first tension spring 321 can also be selected with a longer specification to optimize the effect of applying tension to the friction unit 31 .
  • a specific implementation manner of the above-mentioned friction unit 31 may adopt the structure shown in FIG. 7 to FIG. 10 .
  • the section of the middle space 33 is polygonal.
  • the shape of the bushing 70 can be easily adapted to the middle space 33 .
  • the middle space 33 is just in contact with the outer peripheral side wall of the sleeve 70; At this time, the friction unit 31 is separated from the drive of the shaft sleeve 70 , and the rotation speed is correspondingly lower than that of the shaft sleeve 70 , that is, the shaft sleeve 70 rotates faster, and there is a speed difference between the shaft sleeve 70 and the friction unit 31 .
  • This speed difference makes the shaft sleeve 70 and the middle space 33 produce a certain misalignment, until each edge of the shaft sleeve 70 is correspondingly stuck on each surface of the middle space 33 (from a two-dimensional perspective, that is, each side of the shaft sleeve 70 vertices are stuck on each side of the section polygon), so that it is snapped with the friction unit 31 again in this form.
  • the shaft sleeve 70 can still transmit the driving force to the friction unit 31 , so that the friction disk maintains a certain rotation speed, and the friction units 31 maintain a state of being separated from each other.
  • the outer arc surface of the friction element 31 is always in contact with the inner wall of the first installation space 11 (that is, the inner peripheral surface of the yoke core 10 ), and there is always frictional braking until the rotational speed drops to zero.
  • the bushing 70 is clamped with each friction unit 31, so that the friction unit 31 cannot be pulled back by the first tension spring 321;
  • the unit 31 returns to the normal state, and the shaft sleeve 70 can be rotated in the opposite direction, so that the shaft sleeve 70 is no longer engaged with the friction unit 31 , and the friction unit 31 can be pulled back by the first tension spring 321 .
  • the structure provided by this embodiment can provide extra braking force and enhance the reliability of the brake when the friction disc 30 runs at high speed and the normal braking function fails.
  • a side of the friction unit 31 close to the middle space 33 is a plane.
  • the number of friction units 31 is greater than or equal to three, and the number of friction units 31 is equal to the number of sides of the polygonal section of the middle space 33 . That is, if the number of friction elements 31 is four, the cross section of the middle space 33 is a quadrilateral.
  • the cross-section of the middle space 33 may also be circular, and at this time, the shaft sleeve 70 and the friction disc 30 may cooperate through teeth.
  • the gear sleeve 70 and the friction disc 30 in tooth shape can satisfy a stable fit relationship, and when the above-mentioned middle space 33 is a polygon, the clamping of the hub 70 and the friction disc 30 requires reversing the hub 70 .
  • an alternative implementation of the above-mentioned elastic component 32 may adopt the structures shown in FIGS. 11 to 14 .
  • the elastic assembly 32 includes a fixing frame 324 and a second tension spring set.
  • the fixing frame 324 is located in the middle space 33 , and the interior of the fixing frame 324 forms a fitting space for the sleeve.
  • the second extension spring group is connected between the friction unit 31 and the fixed frame 324 (that is, one end of the second extension spring group is connected to the friction unit 31, and the other end is connected to the fixed frame 324), and the second extension spring group includes at least one second Extension spring 322.
  • the fixing frame 324 cooperates with the shaft sleeve 70 .
  • the tension of the second tension spring 322 is greater than the centrifugal force of each friction element 31 , and the side of the friction element 31 close to the middle space 33 is attached to the outer peripheral surface of the fixed frame 324 .
  • the pulling force of the second tension spring 322 is smaller than the centrifugal force of each friction unit 31, and the friction unit 31 moves away from the middle space 33 in the radial direction of the yoke core 10, and the friction unit 31 A side close to the middle space 33 is separated from the outer peripheral surface of the fixing frame 324 .
  • the friction unit 31 approaches or moves away from the middle space 33 dynamically. Moreover, when the friction unit 31 moves away from the middle space 33 in the radial direction of the yoke core 10, the outer diameter of the entire friction disc 30 becomes larger, and the outer circumference of the friction disc 30 contacts the inner wall of the first installation space 11 (that is, the yoke The inner peripheral surface of the iron core 10) generates a friction torque, thereby reducing the rotational speed of the friction disc 30 and the shaft.
  • the section of the fixing frame 324 may be circular or polygonal.
  • the plurality of second tension springs 322 are evenly distributed around the axial direction of the fixing frame 324 .
  • a plurality of second extension spring groups and a side of the fixed frame 324 far away from the middle space 33 are provided in one-to-one correspondence .
  • each second tension spring set is located in the middle of the outer surface of the corresponding fixing frame 324 .
  • an improved implementation of the above-mentioned elastic component 32 including the fixing frame 324 and the second tension spring group may adopt the structure shown in FIG. 12 and FIG. 14 .
  • the elastic component 32 further includes a guide post 323 whose end is fixedly connected to the fixing frame 324 , and the guide post 323 extends along the radial direction of the yoke core 10 .
  • a side of the friction unit 31 close to the middle space 33 is provided with a slide groove 312 that is slidingly matched with the guide post 323 .
  • the guide post 323 may be a pin, and the pin cooperates with the slide groove 312 .
  • the matching form of the guide post 323 and the slide groove 312 provided in this embodiment is more effective when the section of the fixing frame 324 is polygonal.
  • an improved implementation of the guide post 323 may adopt the structure shown in FIG. 12 and FIG. 14 .
  • each guide post 323 is located in the middle of a side of the friction unit 31 close to the middle space 33 .
  • the guide post 323 is in the middle position, which helps the stability of the friction unit 31 when moving along the radial direction of the yoke core 10 and optimizes the guiding effect.
  • the second tension spring group includes a plurality of second tension springs 322
  • the plurality of second tension springs 322 are equidistantly distributed along the long side of the side surface of the friction unit 31 .
  • the number of the second extension springs 322 is an even number
  • the number of the second extension springs 322 on both sides of the guide post 323 is the same.
  • the quantity of the second extension spring 322 is an odd number
  • the difference in the quantity of the second extension spring 322 on both sides of the guide post 323 is 1;
  • the extension spring 322 is sheathed on the guide post 323 .
  • the second extension spring 322 sleeved on the guide post 323 is located in the sliding slot 312 , and shares the sliding slot 312 with the guiding post 323 .
  • an improved implementation of the installation of the above-mentioned second tension spring 322 may adopt the structures shown in FIG. 12 to FIG. 13 .
  • a second accommodating groove 313 is formed on a side of the friction unit 31 close to the middle space 33 .
  • Two ends of the second tension spring 322 are fixedly connected to the bottom of the second accommodating groove 313 and the outer peripheral surface of the fixing frame 324 respectively.
  • the tension of the second extension spring 322 is greater than the centrifugal force of the friction unit 31 , and the friction unit 31 and the fixed frame 324 are close to each other.
  • the second extension spring 322 is between the friction unit 31 and the fixed frame 324, there will be a gap between the friction unit 31 and the fixed frame 324, and the second extension spring 322 The length should not be too long.
  • the second tension spring 322 is in the second accommodating groove 313 when the rotational speed does not exceed the preset value, so that the friction unit 31 and the fixed frame 324 can be tightly attached to improve the friction Integrity of disc 30.
  • the second extension spring 322 can also be selected with a longer specification to optimize the effect of the reciprocating movement of the friction unit 31 .
  • an improved implementation of the above-mentioned friction unit 31 may adopt the structures shown in FIGS. 7 to 14 .
  • a raised portion 314 is provided on a side of the friction unit 31 away from the middle space 33 .
  • the thickness dimension of the friction disc 30 and the flatness requirements of the two surfaces are very high.
  • the raised portion 314 when overspeed braking occurs (that is, when the friction unit 31 is away from the middle space, and the outer peripheral surface of the friction disc 30 rubs against the inner wall of the yoke core 10), the outer edge of the friction disc 30 will be The abrasion may affect the flatness and radius of the two surfaces of the friction disc 30 and the thickness of the outer ring of the friction disc 30, thereby affecting the braking effect.
  • the raised portion 314 when the friction unit 31 moves away from the middle space 33, the raised portion 314 on the outer periphery of the friction unit 31 first contacts the inner wall of the first installation space 11 (that is, the inner wall of the yoke core 10). peripheral surface), so that the raised portion 314 is preferentially worn, and the flatness and radius of the other two working surfaces of the friction disc 30 and the thickness of the outer ring of the friction disc 30 are not affected, thereby maintaining a good braking effect.

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Abstract

一种制动器，包括磁轭铁芯（10）、活动板（20）、摩擦盘（30）、线圈（40）、衔铁（50）以及弹性件（60），磁轭铁芯（10）由内向外依次同心分布有第一安装空间（11）和第二安装槽（12），第一安装空间（11）沿磁轭铁芯（10）的轴向贯通磁轭铁芯（10）的中心位置，第二安装槽（12）的开口朝向磁轭铁芯（10）的第二轴端；活动板（20）位于第一安装空间（11）内，且靠近磁轭铁芯（10）的第一轴端；摩擦盘（30）设于第一安装空间（11）内，且位于活动板（20）靠近第二轴端的一侧；线圈（40）设于第二安装槽（12）内；衔铁（50）位于磁轭铁芯（10）的第二轴端，衔铁（50）与活动板（20）之间通过连接件（80）连接；弹性件（60）具有使衔铁（50）远离磁轭铁芯（10）的预紧力，本制动器厚度较薄。

Description

制动器
本专利申请要求于2021年09月18日提交的中国专利申请No.CN202111100757.4的优先权。在先申请的公开内容通过整体引用并入本申请。
技术领域
本申请属于机械制动技术领域，具体涉及一种制动器。
 背景技术
制动器有开放式和封闭式，不管是开放式还是封闭式，主要零件的装配方式为堆叠式，即磁轭、衔铁、摩擦盘和尾板依次堆叠，虽然结构简单，但是整体较厚。
随着对电磁制动器的技术要求越来越高，厚度逐渐成为衡量制动器性能的关键参数，特别是一些特殊应用场合，要求制动器整体厚度必须很小，传统堆叠式结构制动器已经无法满足要求。只能依靠使用更好的材料和更精细的工艺尽量压缩上述零件的厚度，以减少总堆叠厚度，这就不可避免的产生其他方面的不足：
（1）如果磁轭厚度减薄会导致线圈空间减小，减弱线圈磁场或增大线圈发热功率；
（2）衔铁、摩擦盘和尾板的厚度减薄后（增大了直径厚度比），整体刚性减弱，容易产生蠕变，或在工作中产生应力变形或热应力变形，零件在制动过程中升温快（因为材料少，热容量小），容易发生制动力矩衰减甚至彻底损坏制动器；
（3）摩擦盘厚度减薄后，结构强度不足，加工难度增大，中孔与摩擦表面垂直度较差，而且与轴或轴套的配合长度小，摩擦盘在旋转过程中易产生摆动，发出异响，增大拖曳力矩；高速旋转时，摩擦盘表面也容易被局部烧蚀，从而降低摩擦力矩，影响制动效果及安全性；
（4）极薄的摩擦副零件（衔铁、摩擦盘、尾板）在摩擦时会放大噪声（类似喇叭振膜的作用）或使噪声更尖锐；
（5）摩擦盘摩擦半径大，相同电机转速下的摩擦线速度高，有时会超过材料适宜的工作线速度，增大磨损率，降低制动效果；
（6）摩擦盘与衔铁和尾板摩擦，衔铁的精度要求较高；为了满足容易磁化和退磁的磁性要求，衔铁必须使用软磁材料制造；摩擦产生的高温和形变会影响衔铁的磁性能。
图15为现有技术中一种制动器的结构示意图。该制动器包括磁轭91、衔铁94、摩擦盘96和尾板95，它们沿被制动轴的轴线X所示的方向，依次堆叠设置。
图15所示的制动器的工作原理为：
被制动轴通过轴套97与摩擦盘96连接。当摩擦盘96自由转动时，被制动轴也能自由转动。当摩擦盘96被衔铁94和尾板95夹紧时，实现制动，被制动轴随摩擦盘96一起停止转动。尾板95通过螺纹连接件98和套筒99与磁轭91连接并保持相对固定。衔铁94可轴向移动，从而改变尾板95与衔铁94之间的距离M。当距离M变大时，摩擦盘96被松开，可以自由转动；当距离M变小时，摩擦盘96被夹紧，实现制动。衔铁94通过线圈92和弹簧93实现轴向移动。当线圈92未通电时，弹簧93推顶衔铁94，使其靠近尾板95，距离M变小，摩擦盘96被夹紧；当线圈92通电时，磁轭91被磁化并吸引衔铁94，使衔铁94克服弹簧92的弹力，远离尾板95，距离M变大，摩擦盘96被松开。
通过图15，结合上述工作原理，很容易理解上述为了减薄总堆叠厚度，其他方面产生的不足：
（1）如果磁轭91的厚度减薄，会导致容纳线圈92的空间减小，线圈92体积减小，磁场减弱或发热功率增大；
（2）衔铁94、摩擦盘96和尾板95的厚度减薄后（增大了直径厚度比），整体刚性减弱，容易产生蠕变，或在工作中产生应力变形或热应力变形，零件在制动过程中升温快（因为材料少，热容量少），容易发生制动力矩衰减，甚至彻底损坏制动器；
（3）摩擦盘96厚度减薄后，结构强度不足，加工难度增大，中孔与摩擦表面垂直度较差，而且与被制动轴或轴套97的配合长度小，摩擦盘96在旋转过程中容易产生摆动，发出异响，增大拖曳力矩；高速旋转时，摩擦盘96表面也容易被局部烧蚀，从而降低摩擦力矩，影响制动效果及安全性；
（4）极薄的摩擦副零件（衔铁94、摩擦盘96、尾板95）在摩擦时会放大噪声（类似喇叭振膜的作用）或使噪声更尖锐；
（5）摩擦盘96摩擦半径变大，相同转速下，摩擦线速度增高，有时会超过材料适宜的工作线速度，增大磨损率，降低制动效果；
（6）摩擦盘96与衔铁94和尾板95摩擦，衔铁94的精度要求较高；为了满足容易磁化和退磁的磁性能要求，衔铁94必须使用软磁材料制造；摩擦产生的高温和形变会影响衔铁94的磁性能。
 技术问题
本申请实施例提供一种制动器，旨在实现制动器的厚度减薄，提高制动器的制动性能。
 技术解决方案
为实现上述目的，本申请采用的技术方案是：提供一种制动器，包括：
磁轭铁芯，由内向外依次同心分布有第一安装空间和第二安装槽，第一安装空间沿所述磁轭铁芯的轴向贯通所述磁轭铁芯的中心位置，所述第二安装槽的开口朝向所述磁轭铁芯的第二轴端；
活动板，位于所述第一安装空间内，且靠近所述磁轭铁芯的第一轴端，所述第一轴端为所述第二轴端的相对端；
摩擦盘，设于所述第一安装空间内，且位于所述活动板靠近所述第二轴端的一侧；
线圈，设于所述第二安装槽内；
衔铁，位于所述磁轭铁芯的第二轴端，所述衔铁与所述活动板之间通过连接件连接，所述连接件贯穿所述磁轭铁芯，且与所述磁轭铁芯滑动配合，所述衔铁可带动所述活动板沿所述磁轭铁芯的轴向移动；以及
弹性件，设于所述衔铁和所述磁轭铁芯之间，所述弹性件具有使所述衔铁远离所述磁轭铁芯的预紧力。
在一种可能的实现方式中，所述磁轭铁芯的第一轴端面形成有定位槽，所述定位槽与所述第一安装空间连通，所述连接件贯穿所述定位槽；
所述活动板的外周设有与所述定位槽对应的定位块，所述定位槽用于避让所述定位块，所述连接件与所述定位块连接。
在一种可能的实现方式中，所述连接件包括导向柱和两个连接部，所述导向柱穿设于所述磁轭铁芯，所述导向柱的一端通过其中一个所述连接部连接于所述活动板，且另一端通过另一个所述连接部连接于衔铁。
在一种可能的实现方式中，所述磁轭铁芯上形成有用于安装所述连接件的环形安装区域，所述安装区域处于所述第一安装空间和所述第二安装槽之间；所述安装区域内还设有安装孔，所述安装孔与所述连接件交替设置。
在一种可能的实现方式中，所述第一安装空间靠近所述第二轴端的内侧面朝向所述磁轭铁芯的轴线延伸的延伸部，所述延伸部的内径小于所述摩擦盘的外径。
在一种可能的实现方式中，所述摩擦盘包括弹性组件以及多个摩擦单体，多个所述摩擦单体绕所述磁轭铁芯的轴线呈环形阵列分布，并围合形成中部空间，所述摩擦单体具有沿所述磁轭铁芯的径向靠近或远离中部空间的自由度，所述弹性组件分别与多个摩擦单体连接，所述弹性组件被配置有使所述摩擦单体靠近中部空间的预紧力。
一些实施例中，所述弹性组件包括多个第一拉簧组，所述第一拉簧组连接于相邻两个所述摩擦单体之间，所述第一拉簧组包括至少一个第一拉簧，所述中部空间形成轴套适配空间。
一些实施例中，所述弹性组件包括：
固定框，位于所述中部空间内，所述固定框的内部形成轴套适配空间；以及
第二拉簧组，连接于所述摩擦单体和所述固定框之间，所述第二拉簧组包括至少一个第二拉簧。
一些实施例中，所述弹性组件还包括端部固接于所述固定框的导柱，所述导柱沿所述磁轭铁芯的径向延伸，所述摩擦单体靠近所述中部空间的一侧设有与所述导柱滑动配合的滑槽。
一些实施例中，所述摩擦单体远离所述中部空间的一侧面设有凸起部。
 有益效果
与现有技术相比，本申请提供的制动器的优点在于：
（1）活动板、摩擦盘以及线圈均处于磁轭铁芯内，因此制动器的整体厚度取决于磁轭铁芯的厚度和衔铁的厚度，即磁轭铁芯和衔铁的厚度的总和，结构紧凑，空间利用率高，厚度较传统堆叠式结构小很多；
（2）摩擦盘、活动板以及线圈均位于磁轭铁芯内部，它们的厚度不会增加制动器的整体厚度，因此摩擦盘、活动板以及线圈的厚度不需要过分压缩，能够保证合理的强度，保证整体刚性，降低产生蠕变的机率，不需要过高的材料和加工成本，保证合适的线圈体积和功率；
（3）摩擦盘的厚度可以适当增加，既能提高摩擦盘的整体结构强度，便于加工，也容易保证中孔与摩擦面的垂直度，增加与轴套或轴的配合长度，减小旋转过程中的抖动、噪音和拖曳力矩；
（4）摩擦盘以及活动板在摩擦的时候由于厚度不至于太薄，降低摩擦产生声音的尖锐度，并且有效减小噪音，特别适于高转速或对静音要求较高的场合；摩擦盘和活动板位于第一安装空间内，制动器工作时，它们被磁轭铁芯和周围的零部件包围，摩擦盘摩擦产生的噪音向外传播受到阻挡，进一步降低了噪音；
（5）摩擦盘处于第一安装空间内，相比于传统摩擦盘直径较小，相同电机转速下的摩擦线速度低，降低磨损率，延长使用寿命；并且摩擦盘直径较小的情况下，与传统的相比，转速相同的情况下，直径较小的摩擦盘的外圈线速度较小，转动惯量减小，从而减少粉尘的甩出；
（6）摩擦盘处于磁轭铁芯的内部，进而摩擦盘旋转时甩出的粉尘也处于磁轭铁芯的内部，有利于工作环境的整洁，还可以避免粉尘进入磁轭铁芯与衔铁之间的间隙；
（7）摩擦盘不与衔铁直接接触，衔铁的精度要求较低，降低了衔铁的制造成本；衔铁也不必使用软磁材料制造，设计时可在更广的范围选择材料，降低了衔铁的设计成本；摩擦盘与活动板及与活动板配合夹紧摩擦盘的结构摩擦实现刹车，与活动板配合夹紧摩擦盘的结构一般为固定结构，且摩擦盘和活动板的直径均较小，工作时稳定性好，制造时精度容易保证，制造成本低；活动板不必使用软磁材料，设计成本也低；高温和少量变形不会影响活动板的正常工作，制动器使用过程中，活动板具有更好的可靠性。
 附图说明
为了更清楚地说明本申请实施例中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动性的前提下，还可以根据这些附图获得其他的附图。
图1为本申请实施例提供的制动器的主视结构示意图；
图2为沿图1中A-A线的剖视结构示意图；
图3为沿图1中B-B线的剖视结构示意图；
图4为本申请实施例提供的制动器的爆炸结构示意图一；
图5为本申请实施例提供的制动器的爆炸结构示意图二；
图6为本申请实施例提供的制动器采用的磁轭铁芯的剖视结构示意图；
图7为本申请实施例提供的制动器采用的摩擦盘的立体结构示意图；
图8为本申请实施例提供的制动器采用的摩擦盘的剖视结构示意图；
图9为本申请实施例提供的制动器采用的摩擦单体的立体结构示意图；
图10为本申请实施例提供的制动器采用的摩擦盘的使用状态示意图；
图11为本申请实施例提供的制动器采用的摩擦盘的立体结构示意图；
图12为本申请实施例提供的制动器采用的摩擦盘的剖视结构示意图；
图13为本申请实施例提供的制动器采用的摩擦单体的立体结构示意图；
图14为本申请实施例提供的制动器采用的摩擦盘的使用状态示意图；
图15为现有技术中堆叠式的制动器的结构示意图。
附图标记说明：
10-磁轭铁芯；11-第一安装空间；12-第二安装槽；13-延伸部；14-连接孔；15-安装孔；16-盲孔；17-定位槽；18-安装区域；20-活动板；21-定位块；30-摩擦盘；31-摩擦单体；311-第一容置槽；312-滑槽；313-第二容置槽；314-凸起部；32-弹性组件；321-第一拉簧；322-第二拉簧；323-导柱；324-固定框；33-中部空间；40-线圈；50-衔铁；60-弹性件；70-轴套；80-连接件；81-连接部；82-导向柱。
本申请的实施方式
为了使本申请所要解决的技术问题、技术方案及有益效果更加清楚明白，以下结合附图及实施例，对本申请进行进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本申请，并不用于限定本申请。
请一并参阅图1至图14，现对本申请提供的制动器进行说明。所述制动器，包括磁轭铁芯10、活动板20、摩擦盘30、线圈40、衔铁50以及弹性件60，磁轭铁芯10由内向外同心分布有第一安装空间11和第二安装槽12，第一安装空间11沿磁轭铁芯10的轴向贯通磁轭铁芯10的中心位置，第二安装槽12的开口朝向磁轭铁芯10的第二轴端；活动板20位于第一安装空间11内，且靠近磁轭铁芯10的第一轴端，第一轴端为第二轴端的相对端；摩擦盘30设于第一安装空间11内，且位于活动板20靠近第二轴端的一侧；线圈40设于第二安装槽12内；衔铁50位于磁轭铁芯10的第二轴端，衔铁50与活动板20之间通过连接件80连接，连接件80贯穿磁轭铁芯10，且与磁轭铁芯10滑动配合，衔铁50可带动活动板20沿磁轭铁芯10的轴向移动；弹性件60设于衔铁50和磁轭铁芯10之间，弹性件60具有使衔铁50远离磁轭铁芯10的预紧力。
需要说明的是，磁轭铁芯10的轴向即磁轭铁芯10的厚度方向。磁轭铁芯10组成制动器后，被制动轴的轴线沿磁轭铁芯10的厚度方向穿过磁轭铁芯10的中心。也就是说，沿磁轭铁芯10的厚度方向穿过磁轭铁芯10的中心线，与被制动轴的轴线重合。第一轴端即磁轭铁芯10的第一侧，第二轴端即磁轭铁芯10的第二侧，该第一侧和第二侧为磁轭铁芯10的沿自身厚度方向分布的不同侧。第二安装槽12也可以称为第二安装空间。磁轭铁芯10也可以被称作磁轭或者外壳。磁轭铁芯10本身不具有磁性，但是当线圈40通电时，磁轭铁芯10被磁化，产生磁性；当线圈40不通电时，磁轭铁芯10的磁性消失。
本申请提供的制动器，在使用的时候，线圈40与外界的电源电连接。向线圈40内通电的时候，磁轭铁芯10和衔铁50在线圈40的激励下产生相互吸引的磁力，磁力将衔铁50吸合，衔铁50靠近第一轴端移动，压缩弹性件60，同时带动活动板20背离第二轴端移动，活动板20背离第二轴端移动的过程中，释放了摩擦盘30，端面不再挤压于摩擦盘30，同时摩擦盘30也不再挤压于与活动板20配合夹紧摩擦盘30的结构，完成释放过程，此时摩擦盘30与轴或轴套70配合，正常转动；当断电的时候，磁轭铁芯10和衔铁50上的磁力消失，弹性件60释放推动衔铁50，衔铁50背离第一轴端移动，同时带动活动板20朝向第二轴端移动，活动板20的端面挤压在摩擦盘30上，同时摩擦盘30的另一个端面挤压在与活动板20配合夹紧摩擦盘30的结构上，由于摩擦阻力，摩擦盘30的转速逐渐下降，直至降为0，完成刹车过程。
与现有技术相比，本实施例提供的制动器的优点在于：
（1）活动板20、摩擦盘30以及线圈40均处于磁轭铁芯10内，因此制动器的整体厚度取决于磁轭铁芯10的厚度和衔铁50的厚度，即磁轭铁芯10和衔铁50的厚度的总和，结构紧凑，空间利用率高，厚度较传统堆叠式结构小很多；
（2）摩擦盘30、活动板20以及线圈40均位于磁轭铁芯10的内部，它们的厚度不会增加制动器的整体厚度，因此摩擦盘30、活动板20以及线圈40的厚度不需要过分压缩，能够保证合理的强度，保证整体刚性，降低产生蠕变的机率，不需要过高的材料和加工成本，保证合适的线圈40体积和功率；
（3）摩擦盘30的厚度可以适当增加，既能提高摩擦盘30的整体结构强度，便于加工，也容易保证中孔与摩擦面的垂直度，增加与轴套70或轴的配合长度，减小旋转过程中的抖动、噪音和拖曳力矩；
（4）摩擦盘30以及活动板20在摩擦的时候由于厚度不至于太薄，降低摩擦产生声音的尖锐度，并且有效减小噪音，特别适于高转速或对静音要求较高的场合；摩擦盘30和活动板20位于第一安装空间11内，制动器工作时，它们被磁轭铁芯10和周围的零部件包围，摩擦盘30摩擦产生的噪音向外传播受到阻挡，进一步降低了噪音；
（5）摩擦盘30处于第一安装空间11内，相比于传统摩擦盘30直径较小，相同电机转速下的摩擦线速度低，降低磨损率，延长使用寿命；并且摩擦盘30直径较小的情况下，与传统的相比，转速相同的情况下，直径较小的摩擦盘30的外圈线速度较小，转动惯量减小，从而减少粉尘的甩出；
（6）摩擦盘30处于磁轭铁芯10的内部，进而摩擦盘30旋转时甩出的粉尘也处于磁轭铁芯10的内部，有利于工作环境的整洁，还可以避免粉尘进入磁轭铁芯10与衔铁50之间的间隙；
（7）本实施例中，摩擦盘30不与衔铁50直接接触，衔铁50的精度要求较低，降低了衔铁50的制造成本；衔铁50也不必使用软磁材料制造，设计时可在更广的范围选择材料，降低了衔铁50的设计成本；摩擦盘30与活动板20及与活动板20配合夹紧摩擦盘30的结构摩擦实现刹车，与活动板20配合夹紧摩擦盘30的结构一般为固定结构，且摩擦盘30和活动板20的直径均较小，工作时稳定性好，制造时精度容易保证，制造成本低；活动板20不必使用软磁材料，设计成本也低；高温和少量变形不会影响活动板20的正常工作，制动器使用过程中，活动板20具有更好的可靠性。
在一些实施例中，上述活动板20的一种具体实施方式可以采用如图2、图5及图6所示结构。参见图2、图5及图6，磁轭铁芯10的第一轴端面形成有定位槽17，定位槽17与第一安装空间11连通，连接件80贯穿定位槽17；活动板20的外周设有与定位槽17对应的定位块21，定位槽17用于避让定位块21，连接件80与定位块21连接。活动板20在安装的时候，定位块21处于定位槽17内，可以起到防呆的作用，方便安装。
所谓防呆是指定位块21与定位槽17的配合产生限制作用。安装活动板20时，操作者不需要花费注意力，也不需要经验与专业知识，即可直接无误的完成正确的操作，从而方便活动板20的安装。
需要说明的是，由于活动板20需要在衔铁50的带动下沿磁轭铁芯10的轴向移动，定位槽17的深度大于定位块21的厚度。连接件80的一端与衔铁50连接，另一端与定位块21连接。
定位槽17深浅的设计标准主要由活动板20的轴向移动距离决定。活动板20的轴向移动距离=导向柱82的长度-摩擦盘30的厚度-延伸部13的厚度。定位槽17的深度≥活动板20的轴向移动距离+活动板20的厚度。以上讨论的定位槽17的深度，前提是活动板20始终位于第一安装空间11内，即活动板20即使轴向移动，也不会凸出磁轭铁芯10的表面。有些情况下，制动器的安装空间较为宽松，活动板20即使凸出磁轭铁芯10的表面，也不会与其它零件产生干涉。此时，定位槽17的深度可以适当减小，甚至可以为零，即不设置定位槽17。
在一些实施例中，上述定位槽17的一种改进实施方式可以采用如图5所示结构。参见图5，定位槽17设有多个，多个定位槽17绕磁轭铁芯10的轴线（即沿厚度方向穿过磁轭铁芯10的中心线）均匀分布。可选的，定位槽17的数量为三个。连接件80的一端连接定位块21，定位槽17的数量增加，活动板20上的定位块21的数量会相应增加，衔铁50产生的驱动力会更均匀地递到活动板20上，制动效果更好。
图5和图6所示的定位槽17距离第二安装槽12和线圈40较近。这种情况下，由于定位槽17去除了导磁材料，可能会对磁路产生负面影响，因此定位槽17的数量不宜过多。不仅是定位槽17的数量，定位槽17的深度也会对磁路产生负面影响。如果安装区域18径向宽度较大，定位槽17与第二安装槽12和线圈40距离较远的情况下，或者定位槽17的深度较小的情况下，在其它实施例中，定位槽17可以是其它结构。例如，定位槽17可以不再是图5和图6所示的独立、分开的槽，而是一个围绕磁轭铁芯10的中部、与磁轭铁芯10同轴的环形槽。定位槽17的结构形式，可以根据其所处的应用环境灵活设计。
在一些实施例中，上述连接件80的一种具体实施方式可以采用如图2至图5所示的结构。参见图2至图5，连接件80包括导向柱82和两个连接部81。导向柱82穿设于磁轭铁芯10中，导向柱82的一端通过其中一个连接部81连接活动板20；导向柱82的另一端通过另一个连接部81连接衔铁50。导向柱82与磁轭铁芯10滑动配合，两个连接部81则分别与活动板20和衔铁50固定连接。衔铁50带动第一活动板20沿磁轭铁芯10的轴向往复移动时，动作稳定流畅，制动效果好。
一般情况下，导向柱82的轴线与磁轭铁芯10的轴线平行。导向柱82通过两个连接部81分别固定连接活动板20和衔铁50。连接部81的实现方式不限，例如可以是螺栓、螺钉、销钉和铆钉等。两个连接部81的实现方式是否相同，不作限制；即，两个连接部81可以采用相同的实现方式，也可以采用不同的实现方式。
导向柱82还可以通过焊接或一体成型的方式与活动板20和衔铁50固定连接。作为示例，当采用一体成型的方式时，可以是导向柱82与活动板20一体成型；即导向柱82的一端通过一体成型的方式与活动板20固定连接，导向柱82的另一端通过除一体成型之外的其它方式与衔铁50固定连接。
总而言之，对于导向柱82与活动板20和衔铁50的固定连接方式，本申请不作限制。凡是已知的、未经过创造性劳动得出的固定连接方式，均位于本申请的保护范围内。
在一些实施例中，上述磁轭铁芯10的一种改进实施方式可以采用如图1至图5所示结构。参见图1至图5，磁轭铁芯10上形成有用于安装连接件80的环形安装区域18，安装区域18位于第一安装空间11和第二安装槽12之间；安装区域18内还设有安装孔15，安装孔15与连接件80交替设置。制动器在安装的时候，用户可以在安装孔15内穿入螺栓，并通过该螺栓将制动器安装至外部物体，从而能够使用制动器。由于安装孔15和连接件80交替设置，可以保证制动器安装牢固，从而在使用的时候具有很好的稳定性。
安装至外部物体时，可以以第一轴端的端面作为安装法兰面。此时，可通过穿入安装孔15内的螺栓、销钉和铆钉等连接零件，将制动器固定至外部物体；第一轴端的端面贴靠外部物体。除此之外，还可以在第二轴端实现制动器的安装。此时需要在第二轴端设置凸台，为衔铁50留出轴向移动空间。凸台可以设置在磁轭铁芯10上，并沿磁轭铁芯10的厚度方向向磁轭铁芯10的外侧凸出。凸台的凸出高度大于衔铁50的厚度与衔铁50的轴向移动距离之和。凸台可以与磁轭铁芯10为一体式结构，也可以是分体式结构。凸台除了设置在磁轭铁芯10之外，也可以是单独的零件，还可以设置在外部物体上。凸台可以与外部物体为一体式结构，也可以是分体式结构。
本实施例中，连接件80穿过安装区域18上的连接孔14进行连接。安装孔15与连接件80交替设置，也就是安装孔15与连接孔14交替设置。作为一种替换实施例，安装孔15也可以不与连接孔14交替设置，但是本实施例中的交替设置更利于制动器使用时的稳定性。
在其它的实施例中，安装孔15也可以不在安装区域18中。例如，安装孔15可以位于磁轭铁芯10的外圈；或者，可以在磁轭铁芯10的边缘设置向外部延伸的部分，安装孔15设置在该向外延伸的部分上。安装孔15的位置与制动器的安装环境等因素相关，根据安装环境等因素适应性的修改安装孔15的位置以及结构的技术方案，均位于本申请的保护范围内。
在一些实施例中，上述磁轭铁芯10的一种改进实施方式可以采用如图1至图6所示结构。参见图1至图6，第一安装空间11靠近第二轴端的一侧具有延伸部13。延伸部13自磁轭铁芯10的内壁，向磁轭铁芯10的中心延伸。一般情况下，延伸部13为圆环板状，延伸部13的内径小于摩擦盘30的外径。制动器组装完成后，延伸部13和活动板20分别处于摩擦盘30的两端（即两侧）。在线圈40断电状态下，衔铁50带动活动板20靠近摩擦盘30，摩擦盘30的两轴端面（即两侧表面）分别与活动板20和延伸部13摩擦，实现制动。
前面的实施例提及与活动板配合夹紧摩擦盘的结构，并且未对该结构的具体实现方式作出限定。本实施例中，延伸部13是该结构的一种具体实现方式。延伸部13可以与磁轭铁芯10一体机加工成型，精度高；延伸部13与摩擦盘30的配合精度高，摩擦效果好。
在一些实施例中，上述磁轭铁芯10的一种改进实施方式可以采用如图3至图4所示结构。参见图3至图4，安装区域18内还设有朝向第二轴端开口的盲孔16。盲孔16用于安装弹性件60。在连接孔14分布的环形路径上，每个连接孔14的两侧均开设有盲孔16。在线圈40断电的时候，衔铁50在弹性件60的作用下，带动活动板20挤压摩擦盘30。如果不设置盲孔16，弹簧（即弹性件60，以下均称为弹簧）可以直接设置在衔铁50和磁轭铁芯10之间。但是这种情况下，无法对弹簧进行导向，还会限制弹簧的选用规格；在设置盲孔16的情况下，弹簧处于盲孔16内，盲孔16的内壁在弹簧伸缩的时候可以起到一定的导向作用，并且弹簧可以选用较长的规格，使用寿命更长。
作为举例，每两个安装孔15之间有一个连接孔14，这个连接孔14的两边分别有一个盲孔16，且连接孔14两边的盲孔16也处于两个安装孔15之间。在其它的实施例中，安装孔15、连接孔14和盲孔16的分布可以采用其它形式。安装区域18中孔结构的分布形式可根据应用环境灵活设计。
在一些实施例中，上述摩擦盘30的一种具体实施方式可以采用如图7至图14所示结构。参见图7至图14，摩擦盘30包括弹性组件32以及多个摩擦单体31，多个摩擦单体31绕磁轭铁芯10的轴线呈环形阵列分布，并围合形成中部空间33，摩擦单体31具有沿磁轭铁芯10的径向靠近或远离中部空间33的自由度，弹性组件32分别与多个摩擦单体31连接，弹性组件32被配置有使摩擦单体31靠近中部空间33的预紧力。
在初始状态，每个摩擦单体31相互靠近，当摩擦盘30转速超过预设值时（处于允许转速内，或超出允许转速），摩擦单体31产生的离心力克服弹性组件32上的预紧力，摩擦单体31沿磁轭铁芯10的径向朝向远离中部空间33的方向移动，相邻两个摩擦单体31之间会相互分离产生间隙，整体摩擦盘30的外径增大，摩擦单体31的外弧面抵接在第一安装空间11的内壁，产生摩擦力，达到制动减速的效果。
摩擦盘30通过分体结构，实现在一定转速条件下相邻摩擦单体31的分离，从而增大整个摩擦盘30的外径，使得摩擦单体31的外弧面可以起到制动效果，可以保证制动器在高速运行提供额外的制动功能，增强制动器的安全性。
需要说明的是，摩擦单体31也可以称作单元块。一般情况下，摩擦盘30整体呈圆饼状且具有一定厚度。磁轭铁芯10的轴线也就是沿磁轭铁芯的厚度方向穿过磁轭铁芯10的中心线。弹性组件32分别与多个摩擦单体31连接是指：弹性组件32包括多个弹性件，多个弹性件分别与摩擦单体31连接。
在一些实施例中，上述弹性组件32的一种具体实施方式可以采用如图8及图10所示结构。参见图8及图10，弹性组件32包括多个第一拉簧组，第一拉簧组连接于相邻两个摩擦单体31之间，第一拉簧组包括至少一个第一拉簧321，中部空间33形成轴套适配空间。每个第一拉簧321分别固定在相邻两个摩擦单体31之间的位置，相邻两个摩擦单体31之间可以通过一个第一拉簧321连接，也可以通过两个第一拉簧321连接（即一个第一拉簧组包括两个第一拉簧321），以此类推；第一拉簧321的数量需要考虑到结构的强度以及需要对应多大的转速时摩擦单体31分开。本实施例中的第一拉簧321不仅结构简单，方便安装。
可以理解的是，第一拉簧321不能凸出于摩擦单体31沿磁轭铁芯10轴向的两端面，否则会影响摩擦盘30的两轴端面的制动效果。
本实施例中，每个第一拉簧321的两端分别连接相邻的两个摩擦单体31。对单个摩擦单体31进行受力分析，其两侧分别受到第一拉簧321的拉力。该拉力具有两个分力，一个是指向圆心的径向力，另一个是垂直于该径向力的周向力。对于摩擦单体31不同侧的第一拉簧321，它们的周向力大小相等，方向相反，相互抵消；而它们的径向力则方向相同，均沿半径方向指向圆心，形成使摩擦单体31向中部空间33移动的合力。
在一些实施例中，上述摩擦单体31的一种改进实施方式可以采用如图8至图9所示结构。参见图8至图9，摩擦单体31的对应面开设有第一容置槽311，对应面为靠近相邻摩擦单体31的一侧面，第一拉簧321的两端分别固接于两相邻摩擦单体31上第一容置槽311的槽底。
如果不设置第一容置槽311，第一拉簧321处于相邻两个摩擦单体31之间，即使在转速没有超出预设值的时候，第一拉簧321也会使得相邻摩擦单体31之间存有一定的间隙，而且第一拉簧321的长度也不能过长。设置第一容置槽311的情况下，第一拉簧321在转速没有超出预设值的时候可以处于第一容置槽311内，相邻的摩擦单体31可以通过侧面相互贴靠，有利于提高摩擦盘30的整体性；而且第一拉簧321也可选用较长的规格，优化对摩擦单体31施加拉力的效果。
在一些实施例中，上述摩擦单体31的一种具体实施方式可以采用如图7至图10所示结构。参见图7至图10，中部空间33的断面为多边形。当摩擦单体31围合形成的中部空间33（即轴套适配空间）为多边形的时候，轴套70的外形很容易适配该中部空间33。当转速低的时候，中部空间33刚好与轴套70的外周侧壁贴合；当转速过高的时候，相邻摩擦单体31分离，从而使得中部空间33大于轴套70的外径。此时摩擦单体31脱离轴套70的带动，转速相比于轴套70会相应降低，即轴套70旋转较快，轴套70与摩擦单体31之间存在转速差。该转速差使得轴套70与中部空间33产生一定的错位，直至轴套70的每个棱边对应卡在中部空间33的每个面上（从二维角度来说，就是轴套70的每个顶点卡在了断面多边形的每个边上），从而以这种形态再次与摩擦单体31卡接。在该形态下，轴套70仍能向摩擦单体31传递驱动力，使摩擦盘保持一定转速，摩擦单体31维持相互分离的状态。在该状态下，摩擦单体31的外弧面始终接触第一安装空间11内壁（即磁轭铁芯10的内周面），始终存在摩擦制动直至转速降为0。在一种特殊情况下，可能会导致转速减小后，轴套70与撑开的各个摩擦单体31卡紧，使得摩擦单体31无法被第一拉簧321拉回；此时如果需要摩擦单体31恢复正常状态，可以反向转动轴套70，使轴套70不再卡接摩擦单体31，摩擦单体31能够被第一拉簧321拉回。
本实施例提供的结构，可以在摩擦盘30高速运行且正常制动功能失效时，提供额外的制动力，增强制动器的可靠性。
可选的，摩擦单体31靠近中部空间33的一侧面为平面。摩擦单体31的数量大于等于3个，摩擦单体31的数量与中部空间33多边形断面的边的数量相等。即如果摩擦单体31的数量为四个，则中部空间33的断面为四边形。
作为另一种可选实施例，中部空间33的断面也可以为圆形，此时轴套70与摩擦盘30可通过齿状配合。齿状配合的轴套70和摩擦盘30可满足稳定的配合关系，并且不会出现上述中部空间33为多边形的时候，轴套70与摩擦盘30卡紧需要反转轴套70的情况。
在一些实施例中，上述弹性组件32的一种替换实施方式可以采用如图11至图14所示结构。参见图11至图14，弹性组件32包括固定框324以及第二拉簧组。固定框324位于中部空间33内，固定框324的内部形成轴套适配空间。第二拉簧组连接于摩擦单体31和固定框324之间（即第二拉簧组的一端连接摩擦单体31，另一端连接固定框324），第二拉簧组包括至少一个第二拉簧322。固定框324与轴套70配合。当转速低于预设值的时候，第二拉簧322拉力大于每个摩擦单体31的离心力，摩擦单体31靠近中部空间33的一侧面贴合于固定框324的外周面。当转速高于预设值的时候，第二拉簧322的拉力小于每个摩擦单体31的离心力，摩擦单体31沿磁轭铁芯10的径向背离中部空间33移动，摩擦单体31靠近中部空间33的一侧面与固定框324的外周面分离。这样，随着被制动轴转速的变化，沿磁轭铁芯10的径向，摩擦单体31动态地靠近或远离中部空间33。并且，在摩擦单体31沿磁轭铁芯10的径向背离中部空间33移动的时候，整个摩擦盘30的外径变大，摩擦盘30的外周接触第一安装空间11内壁（即磁轭铁芯10内周面）产生摩擦力矩，从而降低摩擦盘30和轴的转速。
可选的，固定框324的断面可以为圆形或多边形。当固定框324的断面为圆形的时候，多个第二拉簧322绕固定框324的轴向均匀分布。当固定框324的断面为多边形的时候，多个第二拉簧组与固定框324远离中部空间33的一侧面（固定框324的断面为几边形，则对应几个侧面）一一对应设置。并且，每个第二拉簧组位于对应固定框324外侧面的中间位置。
在一些实施例中，上述弹性组件32包括固定框324和第二拉簧组的一种改进实施方式可以采用如图12及图14所示结构。参见图12及图14，弹性组件32还包括端部固定连接于固定框324的导柱323，导柱323沿磁轭铁芯10的径向延伸。摩擦单体31靠近中部空间33的一侧设有与导柱323滑动配合的滑槽312。通过设置导柱323，可以对摩擦单体31的移动进行导向，确保摩擦单体31按照预设的路径移动。防止摩擦单体31移动路径歪斜，增强了摩擦单体31承受干扰的能力，还能在恢复的时候与固定框324的外周面准确对应。
可选的，导柱323可以为销钉，销钉与滑槽312配合。本实施例提供的导柱323与滑槽312的配合形式，在固定框324断面为多边形的时候效果更好。
在一些实施例中，上述导柱323的一种改进实施方式可以采用如图12及图14所示结构。参见图12及图14，每个导柱323处于摩擦单体31靠近中部空间33一侧面的中间位置。导柱323处于中间位置，有助于摩擦单体31在沿磁轭铁芯10的径向移动时的稳定性，优化导向效果。
具体地，当第二拉簧组包含多个第二拉簧322的时候，多个第二拉簧322沿摩擦单体31的该侧面长边等距分布。当第二拉簧322的数量为偶数的时候，导柱323两侧的第二拉簧322数量相同。当第二拉簧322的数量为奇数的时候，导柱323两侧的第二拉簧322数量差值为1；或，导柱323两侧的第二拉簧322数量相同，中间的第二拉簧322套设在导柱323上，此时套设在导柱323上的第二拉簧322处于滑槽312内，与导向柱323共用该滑槽312。
在一些实施例中，上述第二拉簧322安装的一种改进实施方式可以采用如图12至图13所示结构。参见图12至图13，摩擦单体31靠近中部空间33的一侧面还形成有第二容置槽313。第二拉簧322的两端分别固接于第二容置槽313的槽底和固定框324的外周面。当转速没有超出预设值的时候，第二拉簧322的拉力大于摩擦单体31的离心力，摩擦单体31与固定框324相互靠近。如果不设置第二容置槽313，第二拉簧322处于摩擦单体31与固定框324之间，将会使摩擦单体31与固定框324之间存有间隙，而且第二拉簧322的长度也不能过长。在设置第二容置槽313的情况下，第二拉簧322在转速没有超出预设值的时候处于第二容置槽313内，使得摩擦单体31与固定框324可以贴紧，提高摩擦盘30的整体性。而且第二拉簧322也可选用较长的规格，优化摩擦单体31往复移动的效果。
在一些实施例中，上述摩擦单体31的一种改进实施方式可以采用如图7至图14所示结构。参见图7至图14，摩擦单体31远离中部空间33的一侧面设有凸起部314。摩擦盘30的厚度尺寸，以及两个表面的平面度要求非常高。如果不设置凸起部314，当发生超速制动时（即摩擦单体31远离中部空间，摩擦盘30的外周面与磁轭铁芯10的内壁发生摩擦时），摩擦盘30外缘会被磨损，从而可能影响摩擦盘30的两个表面的平面度、半径以及摩擦盘30外圈的厚度，进而影响制动效果。在设置凸起部314的情况下，当摩擦单体31远离中部空间33移动的时候，摩擦单体31外周的凸起部314首先接触第一安装空间11内壁（即磁轭铁芯10的内周面），这样优先磨损凸起部314，摩擦盘30的另外两个工作表面的平面度、半径以及摩擦盘30外圈的厚度不受影响，从而能保持良好的制动效果。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请的保护范围之内。

Claims (15)

  1. 一种制动器，其特征在于，包括：
    磁轭铁芯，由内向外依次同心分布有第一安装空间和第二安装槽，第一安装空间沿所述磁轭铁芯的轴向贯通所述磁轭铁芯的中心位置，所述第二安装槽的开口朝向所述磁轭铁芯的第二轴端；
    活动板，位于所述第一安装空间内，且靠近所述磁轭铁芯的第一轴端，所述第一轴端为所述第二轴端的相对端；
    摩擦盘，设于所述第一安装空间内，且位于所述活动板靠近所述第二轴端的一侧；
    线圈，设于所述第二安装槽内；
    衔铁，位于所述磁轭铁芯的第二轴端，所述衔铁与所述活动板之间通过连接件连接，所述连接件贯穿所述磁轭铁芯，且与所述磁轭铁芯滑动配合，所述衔铁可带动所述活动板沿所述磁轭铁芯的轴向移动；以及
    弹性件，设于所述衔铁和所述磁轭铁芯之间，所述弹性件具有使所述衔铁远离所述磁轭铁芯的预紧力。
  2. 如权利要求1所述的制动器，其特征在于，所述磁轭铁芯的第一轴端面形成有定位槽，所述定位槽与所述第一安装空间连通，所述连接件贯穿所述定位槽；
    所述活动板的外周设有与所述定位槽对应的定位块，所述定位槽用于避让所述定位块，所述连接件与所述定位块连接。
  3. 如权利要求1所述的制动器，其特征在于，所述连接件包括导向柱和两个连接部，所述导向柱穿设于所述磁轭铁芯，所述导向柱的一端通过其中一个所述连接部连接于所述活动板，且另一端通过另一个所述连接部连接于所述衔铁。
  4. 如权利要求1所述的制动器，其特征在于，所述磁轭铁芯上形成有用于安装所述连接件的环形安装区域，所述安装区域处于所述第一安装空间和所述第二安装槽之间；
    所述安装区域内还设有安装孔，所述安装孔与所述连接件交替设置。
  5. 如权利要求1所述的制动器，其特征在于，所述第一安装空间靠近所述第二轴端的内侧面朝向所述磁轭铁芯的轴线延伸的延伸部，所述延伸部的内径小于所述摩擦盘的外径。
  6. 如权利要求1-5中任意一项所述的制动器，其特征在于，所述摩擦盘包括弹性组件以及多个摩擦单体，多个所述摩擦单体绕所述磁轭铁芯的轴线呈环形阵列分布，并围合形成中部空间，所述摩擦单体具有沿所述磁轭铁芯的径向靠近或远离中部空间的自由度，所述弹性组件分别与多个摩擦单体连接，所述弹性组件被配置有使所述摩擦单体靠近中部空间的预紧力。
  7. 如权利要求6中所述的制动器，其特征在于，所述弹性组件包括多个第一拉簧组，所述第一拉簧组连接于相邻两个所述摩擦单体之间，所述第一拉簧组包括至少一个第一拉簧，所述中部空间形成轴套适配空间。
  8. 如权利要求6所述的制动器，其特征在于，所述弹性组件包括：
    固定框，位于所述中部空间内，所述固定框的内部形成轴套适配空间；以及
    第二拉簧组，连接于所述摩擦单体和所述固定框之间，所述第二拉簧组包括至少一个第二拉簧。
  9. 如权利要求8所述的制动器，其特征在于，所述弹性组件还包括端部固接于所述固定框的导柱，所述导柱沿所述磁轭铁芯的径向延伸，所述摩擦单体靠近所述中部空间的一侧设有与所述导柱滑动配合的滑槽。
  10. 如权利要求6所述的制动器，其特征在于，所述摩擦单体远离所述中部空间的一侧面设有凸起部。
  11. 一种制动器，其特征在于，包括：
    磁轭铁芯，具有预设厚度，沿所述磁轭铁芯的厚度方向穿过所述磁轭铁芯的中心线与被制动轴的轴线重合，所述磁轭铁芯上由中心向边缘依次同心分布有第一安装空间和第二安装空间，所述第一安装空间沿所述厚度方向贯穿所述磁轭铁芯的中部；
    活动板；
    摩擦盘，所述摩擦盘和所述活动板均位于所述第一安装空间内，从而不增加所述制动器的整体厚度，所述摩擦盘和所述活动板均从所述磁轭铁芯的第一侧放入所述第一安装空间；
    线圈，位于所述第二安装空间内，所述第二安装空间具有第一开口，所述第一开口朝向所述磁轭铁芯的第二侧，所述第二侧和所述第一侧为所述磁轭铁芯的沿所述厚度方向分布的不同侧；
    衔铁，位于所述磁轭铁芯的第二侧；
    连接件，贯穿所述磁轭铁芯，所述连接件用于连接所述衔铁和所述活动板并带动所述衔铁和所述活动板沿所述厚度方向移动；和
    弹性件，设于所述磁轭铁芯上，所述弹性件作用于所述衔铁，并具有使所述衔铁向所述第二侧移动的弹性力；
    其中：
    在第一状态下，所述线圈不通电，所述衔铁带动所述活动板向所述第二侧移动，所述活动板压紧所述摩擦盘并阻止所述摩擦盘转动；和
    在第二状态下，所述线圈通电，所述衔铁受到磁力驱动，克服所述弹性力，带动所述活动板向所述第一侧移动，从而与所述摩擦盘分离。
  12. 如权利要求11所述的制动器，其特征在于，所述连接件包括导向柱和两个连接部，两个所述连接部分别位于所述导向柱的两端，所述导向柱可滑动的穿设于所述磁轭铁芯中，所述导向柱分别通过两个所述连接部连接所述衔铁和所述活动板。
  13. 如权利要求11所述的制动器，其特征在于，所述磁轭铁芯具有延伸部，所述延伸部自所述第一安装空间的边缘向中心延伸，所述延伸部远离所述第一侧、靠近所述第二侧，所述延伸部的内径小于所述摩擦盘的外径。
  14. 如权利要求11至13任一项所述的制动器，其特征在于，所述摩擦盘包括：
    多个单元块，围绕所述磁轭铁芯的所述中心线呈环形阵列分布，并围合形成中部空间，所述单元块均有沿所述环形阵列的径向靠近或远离所述中部空间的自由度；和
    多个弹性件，每个所述弹性件均连接所述单元块，并具有使所述单元块靠近所述中部空间的预紧力。
  15. 如权利要求14所述的制动器，其特征在于，所述单元块远离所述中部空间的一侧具有弧形面，所述弧形面上具有凸起部，所述单元块沿所述径向远离所述中部空间并到达预设位置后，所述凸起部与所述磁轭铁芯摩擦接触。
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