Axial load decoupling brake

Abstract

This invention discloses an axial load decoupling brake, comprising a magnetic housing and a hub arranged opposite to each other. The hub is used to mate with an external rotating shaft and is configured to rotate relative to the magnetic housing. A magnetizing component for magnetizing the magnetic housing is disposed inside the magnetic housing. An armature is also provided between the magnetic housing and the hub. A permanent magnet with a radial magnetization direction is mounted on the armature. The permanent magnet has an upper pole surface and a lower pole surface with concentrated magnetic flux and the highest magnetic induction intensity. A positioning groove is formed on the magnetic housing, and an elastic body is placed inside the positioning groove. A cylindrical pin extending into the positioning groove is fixedly disposed on the armature. The beneficial effects of this invention are mainly reflected in the following: When the brake is in the braking state, due to the gap between the cylindrical pin and the slider, this gap ensures that the force of the elastic body is isolated during braking and is not transmitted to the hub and rotating shaft through the cylindrical pin and the armature, thereby fundamentally eliminating the additional axial load on the rotating shaft. Therefore, this invention is particularly suitable for high-precision control scenarios.

Description

Technical Field

[0001] This invention relates to the field of brake technology, and more particularly to an axial load decoupling brake. Background Technology

[0002] An electromagnetic brake is a braking actuator that primarily functions to transmit power and control motion in mechanical transmission systems. It is a mechanical component used to stop or decelerate moving parts, also commonly known as a brake or decelerator. It is mainly used in conjunction with motors, typically mounted on the motor's shaft, and is widely applied in machinery used in metallurgy, construction, chemical industry, food processing, machine tools, stage equipment, elevators, ships, and packaging.

[0003] For example, patent publication number CN 207961334 U discloses a high-magnetic, longitudinally mounted permanent magnet brake. In the braking state, the coil is not energized, and under the magnetic force of the permanent magnet, the armature, magnetic housing, and permanent magnet are tightly pressed together. Under the traction of the leaf spring, the bushing cannot rotate. At this time, the bushing still needs to withstand the axial force transmitted from the leaf spring, causing it to bear an additional load. Furthermore, in this structure, the permanent magnet is horizontally positioned, and only a portion of the area with dense magnetic lines of force can be utilized, resulting in low magnetic energy utilization, an unreasonable layout, and significant limitations. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings of the existing technology and provide an axial load decoupling brake.

[0005] The objective of this invention is achieved through the following technical solution: An axial load decoupling brake includes a magnetic housing and a hub disposed opposite to each other. The hub is used to mate with an external rotating shaft and is configured to rotate relative to the magnetic housing. A magnetizing component for magnetizing the magnetic housing is disposed inside the magnetic housing. An armature is also disposed between the magnetic housing and the hub. A permanent magnet with a radial magnetization direction is mounted on the armature. The permanent magnet has an upper pole surface and a lower pole surface with concentrated magnetic flux and the highest magnetic induction intensity. A positioning groove is formed on the magnetic housing, and an elastic body is placed inside the positioning groove. A cylindrical pin extending into the positioning groove is fixedly disposed on the armature. When the magnetic housing is not magnetized, the upper pole surface is close to the hub, and there is a gap between the cylindrical pin and the elastic body. When the magnetic housing is magnetized, the lower pole surface is close to the magnetic housing, and the cylindrical pin applies a force to the elastic body, causing it to deform.

[0006] Preferably, the elastic body includes a spring and a slider, with one end of the spring fixed to the bottom surface of the positioning groove of the magnetic shell and the other end connected to the slider.

[0007] Preferably, the outer diameter of the slider is adapted to the inner diameter of the positioning groove.

[0008] Preferably, a bushing is fixedly disposed in the positioning groove, the outer end face of the bushing is flush with the corresponding surface of the magnetic shell, and the cylindrical pin is slidably disposed in the bushing.

[0009] Preferably, the armature has a set of slots arranged circumferentially thereon, and the permanent magnet is fixedly disposed in the slots.

[0010] Preferably, the permanent magnet is fixed in the slot by high-temperature resistant epoxy resin adhesive.

[0011] Preferably, in the direction facing the hub, the radial outer surface and radial inner surface of the permanent magnet are respectively lower than the corresponding surfaces of the armature.

[0012] Preferably, the magnetization assembly includes a coil frame fixed inside the magnetic shell and a coil wound on the coil frame.

[0013] The beneficial effects of this invention are mainly reflected in: When the brake is in the braking state, the gap between the cylindrical pin and the slider ensures that the force of the elastic body (spring) is isolated and not transmitted to the hub and shaft through the cylindrical pin and armature, thereby fundamentally eliminating the additional axial load on the shaft. Therefore, the present invention is particularly suitable for high-precision control scenarios (such as servo motors and robot joints).

[0014] The upper and lower pole surfaces, as the areas where the magnetic flux of the permanent magnet is concentrated and the magnetic induction intensity is the highest, can act on the hub and the magnetic shell respectively. This design layout is reasonable, makes full use of the magnetic lines of force on the permanent magnet, and avoids waste of resources. Attached Figure Description

[0015] The technical solution of the present invention will be further described below with reference to the accompanying drawings: Figure 1 : A perspective view of a preferred embodiment of the present invention; Figure 2 : Exploded view of a preferred embodiment of the present invention; Figure 3 : A cross-sectional view of a preferred embodiment of the present invention, in which the coil is de-energized; Figure 4 : A cross-sectional view of a preferred embodiment of the present invention, in which the coil is energized; Figure 5 The magnetic field lines simulation diagram of this invention, in which the coil is de-energized; Figure 6 The magnetic field lines of this invention are shown in the simulation diagram. At this time, the coil is energized. Detailed Implementation

[0016] The present invention will now be described in detail with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments are not limited to the present invention, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the scope of protection of the present invention.

[0017] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0018] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0019] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0020] like Figures 1 to 4 As shown, this invention discloses an axial load decoupling brake, including a magnetic housing 1 and a magnetizing assembly 3 disposed therein for magnetizing the magnetic housing. The magnetizing assembly 3 includes a coil frame 31 fixed inside the magnetic housing 1 and a coil 32 wound on the coil frame 31, as well as other necessary electrical components, such as connectors and pins. For example, in this embodiment, a lead frame 39 is provided on one side of the coil frame 31, through which the connection end of the coil can be led out, and a notch 38 is provided on the corresponding magnetic housing 1 for mating with the lead frame 39.

[0021] The magnetic shell 1 has a receiving cavity 19, and the magnetizing component 3 is placed inside the receiving cavity 19. The structure of integrating the skeleton and coil within the receiving cavity allows the coil 32 to be wound neatly and compactly, improving space utilization and facilitating integration into size-sensitive devices such as robot joint motors. Its open cavity structure also promotes heat dissipation. Simultaneously, the coil 32 generates a stable and concentrated driving magnetic field, ensuring precise control over the armature's engagement and disengagement.

[0022] The magnetic housing 1 has a hub 2 on one side, which is opposite to it. The hub 2 has a shaft hole 20 for connecting an external rotating shaft. The external rotating shaft can be the motor shaft of a precision motor or other connecting shafts, all of which fall within the protection scope of this invention.

[0023] An armature 4 is also provided between the magnetic shell 1 and the hub 2. The armature 4, the magnetic shell 1 and the hub 2 are all made of iron material with high magnetic permeability to reduce magnetic resistance and ensure sufficient magnetic force.

[0024] The armature 4 has a set of slots 42 arranged circumferentially thereon, and a permanent magnet 5 is fixedly disposed in each slot 42. The permanent magnet 5 is of grade N35SH and its magnetization direction is radial. Of course, permanent magnets 5 of other shapes or other arrangements are also within the scope of protection of this invention. For example, the permanent magnet 5 may be a single piece of permanent magnet. In addition, the permanent magnet 5 has an upper pole surface 51 and a lower pole surface 52 with concentrated magnetic flux and the highest magnetic induction intensity, such as... Figure 5 As shown, the magnetic induction intensity of the upper and lower pole surfaces reaches 1.85T (red area). It can be seen that the upper and lower pole surfaces, as the areas where the magnetic flux of the permanent magnet is concentrated and the magnetic induction intensity is the highest, can act on the hub and the magnetic shell respectively. This design layout is reasonable, makes full use of the magnetic lines of force on the permanent magnet, and avoids waste of resources.

[0025] In this embodiment, the permanent magnet 5 is fixed to the slot 42 by high-temperature resistant epoxy resin adhesive. As shown in the figure, the permanent magnet is flat, which maximizes the bonding surface and makes the permanent magnet 5 more resistant to axial impact. This adhesive fixing process is simple, can uniformly transmit stress, and can withstand the heat that may be generated during brake operation, ensuring the reliability of braking.

[0026] The upper pole surface 51 and the lower pole surface 52 are respectively lower than the corresponding surfaces of the armature 4, creating a small axial gap between them. This gap ensures physical isolation between the permanent magnet and the shaft hub and magnetic housing when the armature is engaged with them, thus completely avoiding direct contact, collision, or friction between the permanent magnet and the shaft hub and magnetic housing. This not only protects the permanent magnet from mechanical damage, preventing performance degradation or breakage due to impacts, but also eliminates the uncertainty and vibration caused by accidental contact, thereby significantly enhancing the smoothness and consistency of the braking process, ultimately extending product lifespan and improving braking stability.

[0027] The magnetic housing 1 has a positioning groove 11, and an elastic body 12 is built into the positioning groove 11. Specifically, the elastic body 12 includes a spring 13 and a slider 14. One end of the spring 13 is fixed to the inner bottom surface of the positioning groove 11 of the magnetic housing 1, and the other end is connected to the slider 14. The spring 13 provides a stable and controllable elastic force and ensures that the force transmission path is accurate and smooth. In addition, the outer diameter of the slider 14 is adapted to the inner diameter of the positioning groove 11, ensuring that the slider can only slide smoothly along the axial direction in the positioning groove, without radial wobbling or deflection. This improves the accuracy and reliability of the operation, prevents force transmission failure or wear caused by slider jamming or misalignment, and improves the product's lifespan and stability.

[0028] A cylindrical pin 41 is fixedly mounted on the armature 4 and extends into the positioning groove 11. When the armature 4 is in contact with the hub 2, there is a gap between the cylindrical pin 41 and the slider 14. This gap ensures that the force of the elastic body (spring) is isolated during braking and is not transmitted to the hub and shaft through the cylindrical pin and armature, thereby fundamentally eliminating the additional axial load on the shaft. When the armature 4 is in contact with the magnetic shell, the cylindrical pin 41 applies a force to the spring 13, and the spring 13 is in a compressed state.

[0029] A bushing 15 is fixedly installed within the positioning groove 11. The outer end face of the bushing 15 is flush with the corresponding surface of the magnetic housing 1. The cylindrical pin 41 slides through the bushing 15. The bushing provides precise sliding guidance for the cylindrical pin, further ensuring the axial straightness of the pin's movement. Simultaneously, as a wear-resistant component, the bushing protects the magnetic housing body, reduces wear on critical components, and improves the overall durability and precision of the brake.

[0030] The working process of this invention is briefly described below: When the coil 32 is energized, the electromagnetic field generated by the coil 32 is used to weaken the magnetism of the permanent magnet 5 (taking a permanent magnet force of approximately 2000N as an example), such as... Figure 6As shown, the magnetic induction intensity of the permanent magnet 5 is only about 0.09T (that is, the permanent magnetic force of the permanent magnet 5 is close to 0). Since the magnetic shell 1 is in a magnetized state, the electromagnetic force between it and the armature 4 (about 550N) is greater than the force of the spring 13 (400N). Therefore, the armature 4 is precisely pulled towards the magnetic shell 1. During the movement of the armature 4, the cylindrical pin 41 abuts against the slider 14 and applies a force to it, causing the spring to deform until the lower pole surface 52 is closest to the magnetic shell 1 and the surface of the armature 4 is pressed together, disengaging from the hub and achieving release.

[0031] At the instant the coil 32 is de-energized, the magnetic shell 1 is in a demagnetized state, the armature 4 is in close contact with the magnetic shell 1, and the armature 4 is separated from the hub 2. At this time, as Figure 5 As shown, the magnetic induction intensity of the permanent magnet 5 reaches 1.85T. Since the distance between the armature 4 and the magnetic shell 1 is greater than the distance between the armature 4 and the hub 2, the permanent magnetic force between the armature 4 and the magnetic shell 1 is greater than the permanent magnetic force between the armature 4 and the hub 2, and the difference between the two is less than 400N. The spring 13 applies a force to the armature 4, driving the armature 4 to move towards the hub. During the movement, the permanent magnetic force between the armature 4 and the magnetic shell 1 gradually decreases, and the permanent magnetic force between the armature 4 and the hub 2 gradually increases until the end face of the armature 4 and the hub 2 are in contact and braked. At this time, there is a gap between the cylindrical pin 41 and the slider 14.

[0032] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0033] The detailed descriptions listed above are merely specific descriptions of feasible embodiments of the present invention, and are not intended to limit the scope of protection of the present invention. All equivalent embodiments or modifications made without departing from the spirit of the present invention should be included within the scope of protection of the present invention.

Claims

1. An axial load decoupling brake, comprising a magnetic housing (1) and a hub (2) disposed opposite to each other, the hub (2) being used to engage an external rotating shaft and configured to rotate relative to the magnetic housing (1), the magnetic housing (1) having a magnetizing assembly (3) disposed inside for magnetizing it, and an armature (4) further disposed between the magnetic housing (1) and the hub (2), characterized in that: The armature (4) is equipped with a permanent magnet (5) with a radial magnetization direction. The permanent magnet (5) has an upper pole surface (51) and a lower pole surface (52) with concentrated magnetic flux and the highest magnetic induction intensity. The magnetic shell (1) is provided with a positioning groove (11), and an elastic body (12) is built into the positioning groove (11). A cylindrical pin (41) is fixedly provided on the armature (4) and extends into the positioning groove (11). When the magnetic shell (1) is not in a magnetized state, the upper pole surface (51) is close to the hub (2), and there is a gap (40) between the cylindrical pin (41) and the elastic body (12). When the magnetic shell (1) is in a magnetized state, the lower pole surface (52) is close to the magnetic shell (1), and the cylindrical pin (41) applies a force to the elastic body (12) to deform it.

2. The axial load decoupling brake according to claim 1, characterized in that: The elastic body (12) includes a spring (13) and a slider (14). One end of the spring (13) is fixed to the bottom surface of the positioning groove (11) of the magnetic shell (1), and the other end is connected to the slider (14).

3. The axial load decoupling brake according to claim 2, characterized in that: The outer diameter of the slider (14) is adapted to the inner diameter of the positioning groove (11).

4. The axial load decoupling brake according to claim 2, characterized in that: A bushing (15) is fixedly installed in the positioning groove (11). The outer end face of the bushing (15) is flush with the corresponding surface of the magnetic shell (1). The cylindrical pin (41) slides through the bushing (15).

5. The axial load decoupling brake according to claim 1, characterized in that: The armature (4) has a set of slots (42) arranged along its circumference, and the permanent magnet (5) is fixedly installed in the slots (42).

6. The axial load decoupling brake according to claim 5, characterized in that: The permanent magnet (5) is fixed in the slot (42) by high-temperature resistant epoxy resin adhesive.

7. The axial load decoupling brake according to claim 1, characterized in that: In the direction facing the hub (2), the radial outer surface and radial inner surface of the permanent magnet (5) are respectively lower than the corresponding surfaces of the armature (4).

8. The axial load decoupling brake according to claim 1, characterized in that: The magnetization assembly (3) includes a coil frame (31) fixed inside the magnetic shell (1) and a coil (32) wound on the coil frame (31).

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