Brake mechanism, oscillating device and rotating device

Abstract

The application discloses a brake mechanism, a swing device and a rotating device, and belongs to the field of five-axis swing heads. The brake mechanism comprises a piston, an oil cylinder body in driving connection with the piston, and an elastic ring located on the side of the piston away from the oil cylinder body. The elastic ring comprises a locking section, a reset section and a fixing section connected in sequence. The end face of the locking section is matched with the piston, the fixing section is fixedly connected with the oil cylinder body, and the side face of the locking section is used for being matched with a movable member. The reset section is inclined to the vertical direction by a preset angle, and the axial force of the piston on the end face of the locking section is smaller than the radial force generated by the side face of the locking section. The technical effect of the application is that the locking can be realized by using a small hydraulic driving force.

Description

Technical Field

[0001] This invention relates to a five-axis oscillating head, and more particularly to a braking mechanism, an oscillating device, and a rotating device. Background Technology

[0002] A five-axis swivel head is a dual-axis swivel spindle head assembly that is configured on a five-axis machine tool and integrates swivel and rotational degrees of freedom. It can drive the tool to achieve dual-axis attitude deflection and work with the XYZ linear axes of the machine tool to complete spatial five-axis linkage machining.

[0003] The braking mechanism is an important component of a five-axis swivel head, mainly used to lock the swivel or rotating device, thereby increasing the machining stability of the tool. Chinese invention patent CN103128584A, published on June 5, 2013, discloses a locking device for the spindle head of a five-axis swivel head. The direct-drive spindle head is located in the middle of the swivel head box, and the drive torque motor is located on the right side of the swivel head box. The locking device is located on the left side of the swivel head box. A connecting shaft on the left side connects the direct-drive spindle head and the support bearing. A rotating friction ring is connected to the left end face of the connecting shaft. The cylinder body is connected to the swivel head box. Adjusting the adjusting shim under the cylinder body creates a slight gap between the rotating friction ring and the cylinder body. The cylinder cover connects the cylinder body and the deformable friction piston. There is a slight gap between the deformable friction piston, the rotating friction ring, and the cylinder body. This invention has advantages such as simple structure, convenient operation, reliable locking, and accurate positioning. It can significantly improve machining efficiency and may even completely eliminate the investment in some large-scale automated production lines, greatly saving space and the time and cost of transportation between different manufacturing units.

[0004] The shortcoming of this invention is that the force transmission method between the cylinder head, deformable friction piston, rotating friction ring, cylinder body and direct drive spindle head is difficult to amplify the force. That is, the hydraulic driving force generated by the cylinder head and the locking force on the direct drive spindle head are equal. Therefore, a large hydraulic driving force is required to achieve locking, which easily leads to the large size of the related hydraulic system. Summary of the Invention

[0005] Purpose of the invention: The purpose of this invention is to provide a braking mechanism that can achieve locking with only a small hydraulic driving force; another purpose of this invention is to provide a swinging device; another purpose of this invention is to provide a rotating device.

[0006] Technical solution:

[0007] A braking mechanism, comprising:

[0008] piston;

[0009] The cylinder body is driven and connected to the piston;

[0010] An elastic ring located on the side of the piston away from the cylinder body includes a locking section, a reset section, and a fixing section connected in sequence. The end face of the locking section mates with the piston, the fixing section is fixedly connected to the cylinder body, and the side of the locking section is used to mate with a movable component.

[0011] The reset section is inclined at a preset angle to the vertical direction, and the axial force exerted on the end face of the locking section by the piston is less than the radial force generated by the side surface of the locking section.

[0012] Specifically, because the reset section and the vertical direction are inclined at a preset angle θ, the axial force on the end face of the locking section by the piston is less than the radial force generated by the side of the locking section, according to formula F 轴向力 =F 径向力 *tanθ, to achieve an axial force less than the radial force, tanθ should be less than 1. The preset tilt angle θ is in the range of 0°-45°, which means that only a small hydraulic drive axial force is needed to achieve a large radial force clamping, which helps to avoid the need for large hydraulic systems. The preferred value range of the preset tilt angle θ is 12°-16°. If the preset tilt angle θ is less than 12°, although the radial force amplification factor is large, the requirements for the processing accuracy, material and heat treatment of the elastic ring are high. If the preset tilt angle θ is greater than 16°, it is easy to cause the radial force amplification factor to be too small.

[0013] Optionally, the thickness of the locking segment is greater than the thickness of the reset segment to increase the stiffness of the locking segment and the elasticity of the reset segment.

[0014] Optionally, the thickness of the fixed segment is greater than the thickness of the locking segment. In the unlocked state, one end of the locking segment is flush with one end of the fixed segment, and the reset segment is connected between the other end of the locking segment and the other end of the fixed segment.

[0015] Optionally, the end face of the locking section is provided with a boss, which cooperates with the piston to form a mechanical limit.

[0016] Optionally, the reset section is provided with at least one reset section through hole to improve the elasticity of the reset section.

[0017] Optionally, the fixing section is provided with at least one fixing section through hole to reduce the local stiffness of the fixing section; the fixing section is also provided with several mounting holes to accommodate fasteners.

[0018] Optionally, the material of the locking segment has less elasticity than the material of the reset segment.

[0019] Optionally, during locking, the effective frictional locking area of ​​the side of the locking section with the movable member accounts for 72%-88% of the total side area of ​​the locking section.

[0020] A swing device, including a braking mechanism, further comprising:

[0021] A first housing, wherein the cylinder body is connected to the first housing;

[0022] The first motor, the stator of the first motor is connected to the first housing;

[0023] A contact ring is provided between the rotor of the first motor and the side of the locking section, and the contact ring is connected to the first housing.

[0024] The movable components are configured as a first swing body and a second swing body that are mutually driven and connected, wherein the first swing body is connected to the rotor of the first motor.

[0025] A rotating device includes a braking mechanism, a second housing, and a second motor. The cylinder body is connected to the second housing, the stator of the second motor is connected to the second housing, the movable member is configured as a rotating body, the rotor of the second motor is connected to the rotating body, and the side of the locking section cooperates with the rotating body.

[0026] A five-axis oscillating head includes an oscillating device and a rotating device, wherein the rotating body of the rotating device is connected to the first housing of the oscillating device.

[0027] Beneficial effects:

[0028] (1) A braking mechanism according to an embodiment of the present invention, based on formula F 轴向力 =F 径向力 *tanθ, to achieve an axial force less than the radial force, tanθ should be less than 1. The preset tilt angle θ ranges from 0° to 45°, meaning that only a small hydraulic drive axial force is needed to achieve a large radial force clamping, which helps to avoid the need for large-scale hydraulic systems.

[0029] (2) In a brake mechanism according to an embodiment of the present invention, the reset section facilitates the good reset performance of the elastic ring, thereby facilitating rapid reset after the hydraulic oil returns to the cylinder body, and ensuring good reset and unlocking performance of the brake mechanism according to an embodiment of the present invention. Attached Figure Description

[0030] Figure 1 This is a front view of the five-axis oscillating head of Embodiment 1 of the present invention;

[0031] Figure 2 This is a left view of the five-axis oscillating head of Embodiment 1 of the present invention;

[0032] Figure 3 yes Figure 2 Cross-sectional view of section AA;

[0033] Figure 4 yes Figure 3 Partial unlocked state diagram of B;

[0034] Figure 5 yes Figure 3 Diagram of the local locking state of B;

[0035] Figure 6 This is a force analysis diagram of the elastic ring in Embodiment 1 of the present invention;

[0036] Figure 7 yes Figure 3 A partial view of C;

[0037] Figure 8 This is one of the structural diagrams of the elastic ring in Embodiment 1 of the present invention;

[0038] Figure 9 This is a second structural diagram of the elastic ring in Embodiment 1 of the present invention;

[0039] In the diagram: 1. Cylinder body; 2. Piston; 3. Elastic ring; 31. Locking section; 32. Reset section; 33. Fixing section; 35. Boss; 36. Reset section through hole; 37. Fixing section through hole; 38. Mounting hole; 41. First housing; 42. First motor; 43. Contact ring; 44. First swing body; 45. Second swing body; 51. Second housing; 52. Second motor; 53. Rotating body. Detailed Implementation

[0040] To make the technical solution of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0041] The present application will now be described in further detail with reference to the accompanying drawings and embodiments. It is understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, only the parts relevant to the invention are shown in the accompanying drawings. The terms "first," "second," etc., used in this invention are for the convenience of describing the technical solutions of the invention and have no specific limiting effect; they are all general terms and do not constitute a limitation on the technical solutions of the invention. It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of this application can be combined with each other. In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, not to 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. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances. Multiple technical solutions in the same embodiment, as well as multiple technical solutions in different embodiments, can be arranged and combined to form new technical solutions that do not contradict or conflict, all of which are within the scope of protection claimed by this invention.

[0042] Example 1

[0043] like Figures 4-7 This embodiment provides a braking mechanism, including: a piston 2; a cylinder body 1 drivenly connected to the piston 2; and an elastic ring 3 located on the side of the piston 2 away from the cylinder body 1. The elastic ring 3 includes a locking section 31, a reset section 32, and a fixing section 33 connected in sequence. The end face of the locking section 31 cooperates with the piston 2, the fixing section 33 is fixedly connected to the cylinder body 1, and the side of the locking section 31 is used to cooperate with a movable component. The reset section 32 is inclined at a preset angle to the vertical direction, and the axial force on the end face of the locking section 31 from the piston 2 is less than the radial force generated by the side of the locking section 31.

[0044] Specifically, during locking, hydraulic oil is supplied to cylinder 1, causing piston 2 to extend. First, piston 2 contacts the end face of locking section 31. Then, piston 2 moves locking section 31 and reset section 32 away from cylinder 1, causing reset section 32 to bend and deform until piston 2 causes the side of locking section 31 to contact the moving component, thus completing the locking. During unlocking, hydraulic oil is returned to cylinder 1, piston 2 no longer exerts pressure on the end face of locking section 31, and the bent reset section 32 resets, causing locking section 31 to move closer to cylinder 1 and causing the side of locking section 31 to separate from the moving component, thus completing the unlocking.

[0045] The cylinder body 1, in conjunction with the piston 2, facilitates the generation of hydraulic driving force. The reset section 32 ensures good reset performance of the elastic ring 3, thereby facilitating rapid reset after the hydraulic oil returns to the cylinder body 1, ensuring good reset and unlocking performance of the brake mechanism in this embodiment. The fixing section 33 facilitates the fixed connection between the elastic ring 3 and the cylinder body 1, thereby ensuring the stability of the elastic ring 3. The fixing section 33 and the cylinder body 1 are preferably connected by fasteners such as screws, ensuring good detachability of the elastic ring 3, thus facilitating timely maintenance or replacement of the elastic ring 3. The elastic ring 3 can be made of only one material, preferably 60Si2Mn spring steel. In this case, the locking section 31, the reset section 32, and the fixing section 33 are preferably integrally formed. The elastic ring 3 can also be made of multiple materials, i.e., the locking section 31, the reset section 32, and the fixing section 33 are made of different materials. In this case, the locking section 31, the reset section 32, and the fixing section 33 can be fixed by tenons, pins, or interference fits.

[0046] Because the reset section 32 is inclined at a preset angle θ to the vertical direction, so that the axial force on the end face of the locking section 31 by the piston 2 is less than the radial force generated by the side of the locking section 31, firstly, as Figure 6 According to formula F 轴向力 =F 径向力*tanθ, to achieve an axial force less than the radial force, tanθ should be less than 1. The preset tilt angle θ ranges from 0° to 45°, meaning that only a small hydraulic axial force is needed to achieve a large radial force clamping, thus avoiding the need for a large hydraulic system. The preferred preset tilt angle θ range is 12° to 16°. If the preset tilt angle θ is less than 12°, although the radial force amplification factor is large, it places high demands on the machining accuracy, material, and heat treatment of the elastic ring 3. If the preset tilt angle θ is greater than 16°, it easily leads to a too small radial force amplification factor. Secondly, pure axial force locking, i.e., relying on two When the planes are pressed together, they are prone to slippage, creep, and loosening. Radial force expansion and clamping, which is a full-coverage clamping of the circumferential surface (i.e., the side of the locking section 31), includes both geometric constraints and frictional force for dual locking, which helps to ensure high locking and positioning accuracy. Furthermore, with pure axial force locking, the elastic ring 3 has to bend and deform repeatedly and significantly, which is prone to breakage. Radial force expansion and clamping effectively reduces the bending amplitude of the elastic ring 3. Furthermore, with pure axial force locking, once the friction surfaces are engaged, the reset has to overcome huge static friction. With radial force expansion and clamping, the elastic ring 3 only needs to contract slightly to completely disengage immediately, ensuring good reset performance.

[0047] It should be noted that, during locking, the effective friction locking area of ​​the side of the locking section 31 with the moving component accounts for 72%-88% of the total side area of ​​the locking section 31.

[0048] If it is less than 72%, it will lead to excessive local contact pressure: First, when there are slight shape and position errors (such as roundness and cylindricity deviations) on the contact surface, local stress concentration will occur, resulting in surface crushing, wear, and even "point contact" instead of surface contact, which will greatly reduce friction and locking reliability. Second, when the moving component is loaded, the local high pressure will accelerate the fatigue wear of the contact surface, and the locking force will decrease significantly after long-term use.

[0049] If the contact is greater than 88%, complete contact (100%) is theoretically ideal, but it cannot be achieved in actual engineering and will bring new problems: First, the machining and assembly errors cannot be completely eliminated. There will inevitably be slight coaxiality and cylindricity errors between the elastic ring 3 and the moving component. If it is designed to be 100% contact, local interference and misfitting will occur during actual locking, or only local true contact will occur, while the rest of the area will be in a state of loose contact, which will reduce the effective contact area. Second, if the contact area is too large, the frictional resistance of the contact surface will be too large. When locking and unlocking, greater frictional force needs to be overcome, which increases the operating force and is also prone to causing the tilted elastic ring 3 to "self-lock and jam" and fail to reset normally. Furthermore, if the contact area is too large, the wear area of ​​the contact surface will be too dispersed, which will reduce the local pressure and is not conducive to forming a stable friction locking state.

[0050] Furthermore, such as Figures 4-7The thickness of the locking section 31 is greater than the thickness of the reset section 32 to increase the rigidity of the locking section 31 and the elasticity of the reset section 32.

[0051] Specifically, the locking section 31 has a relatively large thickness, while the reset section 32 has a relatively small thickness. This increases the rigidity of the locking section 31, ensuring its resistance to friction and wear, and thus its locking performance. It also increases the elasticity of the reset section 32, reducing bending stiffness and ensuring good elastic reset performance, thus preventing jamming. Preferably, the thickness of the locking section 31 is 2-2.5 times that of the reset section 32. If the thickness difference is too small, deformation may be dispersed in the locking section 31, leading to wear failure and fatigue fracture. If the thickness difference is too large, the reset section 32 may be too thin, resulting in excessive deformation and stress, which may lead to plastic deformation and breakage.

[0052] Furthermore, such as Figures 4-7 The thickness of the fixed section 33 is greater than the thickness of the locking section 31. In the unlocked state, one end of the locking section 31 is flush with one end of the fixed section 33, and the reset section 32 is connected between the other end of the locking section 31 and the other end of the fixed section 33.

[0053] Specifically, the thickness of the fixed section 33 is the greatest, used for positioning the rigid base and bearing force transmission, which helps to ensure good fixing performance of the elastic ring 3 and the cylinder body 1. Since one end of the locking section 31 is flush with one end of the fixed section 33 in the unlocked state, it helps to ensure good stability of the initial state of the elastic ring 3 and prevents initial bending deformation. The reset section 32 is connected between the other end of the locking section 31 and the other end of the fixed section 33, which makes it easy for the preset tilt angle θ of the reset section 32 to be affected by the thickness ratio of the locking section 31 and the fixed section 33. This makes the structural design linkage of the elastic ring 3 good, and at the same time, it helps to ensure good smoothness of the surface of the elastic ring 3 away from the piston 2, preventing stress concentration.

[0054] Furthermore, such as Figures 4-5 The locking section 31 has a boss 35 on its end face, which cooperates with the piston 2 to form a mechanical limit.

[0055] Specifically, when piston 2 is pushed to the locked position, piston 2 and boss 35 cooperate, and elastic ring 3 is pushed to the "over-dead point" position, forming a mechanical limit. Locking is no longer achieved solely by the elasticity of elastic ring 3, which facilitates partial unloading of elastic ring 3, prevents fatigue, and solves the industry common problem of long-term fatigue decay of elastic locking.

[0056] Furthermore, such as Figures 8-9 The reset section 32 is provided with at least one reset section through hole 36 to enhance the elasticity of the reset section 32.

[0057] Specifically, the through hole 36 of the reset section is equivalent to a weight reduction hole, which facilitates the reduction of the bending stiffness of the reset section 32 and improves the elastic reset performance. The shape of the through hole 36 of the reset section is preferably waist-shaped, which facilitates a smooth stress transition without sharp corners, thus providing the best fatigue resistance. It also facilitates uniform stiffness reduction and good linear bending deformation. The number of through holes 36 of the reset section is not limited and can be twelve, fourteen, etc., but is preferably twelve. The spacing between adjacent through holes 36 of the reset section is preferably equal.

[0058] It should be noted that in a braking mechanism of an embodiment of the present invention, the spacing between adjacent reset section through holes 36 (i.e. the length of the connecting rib) is preferably less than the length of the reset section through hole 36. This is to ensure the extremely low stiffness and ultra-large elastic deformation capacity of the reset section 32. Furthermore, due to the presence of the boss 35, locking is no longer achieved solely by the elasticity of the elastic ring 3, and the elastic ring 3 will not be damaged due to its extremely low stiffness. This helps to overcome the technical bias in the industry that "the connecting rib is longer than the hole length".

[0059] Furthermore, such as Figures 8-9 The fixed section 33 is provided with at least one fixed section through hole 37 and several mounting holes 38.

[0060] Specifically, the through hole 37 in the fixed section is used to weaken the local stiffness of the fixed section 33, avoid an excessive difference in stiffness between the fixed section 33 and the reset section 32, achieve a smooth transition of stiffness among the three sections, reduce abrupt stress changes at the root, and prevent stress concentration fracture at the junction of the fixed section 33 and the reset section 32. The through hole 37 in the fixed section is preferably a small round hole to prevent excessive weakening of the overall rigidity of the fixed section 33 and ensure that the underlying logic of stiffness of the fixed section 33 > stiffness of the locking section 31 > stiffness of the reset section 32 is satisfied. The number of through holes 37 in the fixed section is not limited and can be eighteen, twenty, etc., preferably eighteen, and the spacing between adjacent through holes 37 in the fixed section is preferably equal.

[0061] Mounting holes 38 are used to facilitate the detachable and fixed connection between the fixed section 33 and the cylinder body 1 by fasteners such as screws. The mounting holes 38 are preferably stepped holes to prevent interference between fasteners and other related components. The number of mounting holes 38 is not limited and can be six, eight, etc., but is preferably six. The spacing between adjacent mounting holes 38 is preferably equal.

[0062] Furthermore, such as Figures 4-7 The elasticity of the material of the locking section 31 is less than that of the material of the reset section 32.

[0063] Specifically, the locking section 31 has relatively low elasticity, which helps to ensure the locking performance of the locking section 31, while the reset section 32 has relatively high elasticity, which helps to ensure the elastic reset performance of the reset section 32. The locking section 31 can be made of 40Cr or CrMo alloy steel, the reset section 32 can be made of 60Si2Mn or 65Mn, and the fixing section 33 can be made of 45 steel or 40Cr.

[0064] like Figures 3-5 This embodiment also provides a swing device, including a braking mechanism of this embodiment, and further including: a first housing 41, a cylinder body 1 connected to the first housing 41; a first motor 42, the stator of the first motor 42 connected to the first housing 41; a contact ring 43 cooperating between the rotor of the first motor 42 and the side of the locking section 31, the contact ring 43 connected to the first housing 41; wherein the movable components are configured as a first swing body 44 and a second swing body 45 that are mutually driven and connected, the first swing body 44 being connected to the rotor of the first motor 42.

[0065] Specifically, the second swing body 45 is used to hold the cutting tool. During operation, the rotor of the first motor 42 drives the first swing body 44, the second swing body 45 and the cutting tool to swing in sequence.

[0066] The first housing 41 is used to support the cylinder body 1, the first motor 42, the contact ring 43, the first swing body 44, and the second swing body 45, etc.; the rotor of the first motor 42 is used to drive the first swing body 44 to rotate. The number of the first motor 42 and the first swing body 44 is preferably two to facilitate dual drive. The type of the first motor 42 is preferably a torque motor.

[0067] like Figure 3 and Figure 7 This embodiment also provides a rotating device, including a braking mechanism of this embodiment, and further including a second housing 51 and a second motor 52. The cylinder body 1 is connected to the second housing 51, the stator of the second motor 52 is connected to the second housing 51, the movable component is configured as a rotating body 53, the rotor of the second motor 52 is connected to the rotating body 53, and the side of the locking section 31 cooperates with the rotating body 53.

[0068] Specifically, during operation, the rotor of the second motor 52 drives the rotating body 53 to rotate; wherein, the second housing 51 is used to support the cylinder body 1, the second motor 52 and the rotating body 53, etc.; the number of the second motor 52 is preferably one, and the type of the second motor 52 is preferably a torque motor.

[0069] like Figures 1-3 This embodiment also provides a five-axis oscillating head, including an oscillating device and a rotating device, wherein the rotating body 53 of the rotating device is connected to the first housing 41 of the oscillating device.

[0070] Specifically, during operation, the rotating body 53 of the rotating device drives the first housing 41 of the swing device to rotate, which facilitates the completion of spatial five-axis linkage machining in conjunction with the XYZ linear axes of the machine tool.

[0071] The above embodiments merely illustrate several implementation methods of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this patent should be determined by the appended claims.

Claims

1. A braking mechanism, characterized in that, include: Piston (2); The cylinder body (1) is driven and connected to the piston (2); An elastic ring (3) is located on the side of the piston (2) away from the cylinder body (1). The elastic ring (3) includes a locking section (31), a reset section (32), and a fixing section (33) connected in sequence. The end face of the locking section (31) is engaged with the piston (2). The fixing section (33) is fixedly connected to the cylinder body (1). The side of the locking section (31) is used to engage with the movable component. The reset section (32) is inclined at a preset angle to the vertical direction, and the end face of the locking section (31) is subjected to an axial force from the piston (2) that is less than the radial force generated by the side of the locking section (31).

2. The braking mechanism according to claim 1, characterized in that, The thickness of the locking section (31) is greater than the thickness of the reset section (32) to increase the rigidity of the locking section (31) and the elasticity of the reset section (32).

3. A braking mechanism according to claim 2, characterized in that, The thickness of the fixed segment (33) is greater than the thickness of the locking segment (31). In the unlocked state, one end of the locking segment (31) is flush with one end of the fixed segment (33), and the reset segment (32) is connected between the other end of the locking segment (31) and the other end of the fixed segment (33).

4. A braking mechanism according to claim 1, characterized in that, The locking section (31) has a boss (35) on its end face. The boss (35) and the piston (2) cooperate to form a mechanical limit.

5. A braking mechanism according to claim 1, characterized in that, The reset section (32) is provided with at least one reset section through hole (36) to enhance the elasticity of the reset section (32).

6. A braking mechanism according to claim 1, characterized in that, The fixing section (33) is provided with at least one fixing section through hole (37) to reduce the local stiffness of the fixing section (33); the fixing section (33) is also provided with a plurality of mounting holes (38) to accommodate fasteners.

7. A braking mechanism according to claim 1, characterized in that, The elasticity of the material of the locking section (31) is less than that of the material of the reset section (32).

8. A braking mechanism according to claim 1, characterized in that, When locked, the effective frictional locking area of ​​the side of the locking section (31) with the movable member accounts for 72%-88% of the total side area of ​​the locking section (31).

9. A swinging device, characterized in that, Including a braking mechanism as described in any one of claims 1-8, further comprising: The first housing (41) is connected to the cylinder body (1); The first motor (42) has its stator connected to the first housing (41); A contact ring (43) is provided between the rotor of the first motor (42) and the side of the locking section (31), and the contact ring (43) is connected to the first housing (41); The movable components are configured as a first swing body (44) and a second swing body (45) that are mutually driven and connected, wherein the first swing body (44) is connected to the rotor of the first motor (42).

10. A rotating device, characterized in that, The braking mechanism includes any one of claims 1-8, and further includes a second housing (51) and a second motor (52), wherein the cylinder body (1) is connected to the second housing (51), the stator of the second motor (52) is connected to the second housing (51), the movable member is configured as a rotating body (53), the rotor of the second motor (52) is connected to the rotating body (53), and the side of the locking section (31) cooperates with the rotating body (53).

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