Torque limiter

Abstract

A torque limiter includes: a torque input mechanism, a torque output mechanism, balls, and a torque adjustment assembly. The outer peripheral wall of the torque input mechanism is provided with a toothed meshing part, and the outer peripheral wall of the toothed meshing part is provided with a ball groove, in which the balls are disposed. The end face of the first end of the torque output mechanism is provided with a slot corresponding to the number of balls, and each slot can be aligned with a ball groove, with the balls partially accommodated in the slot. A bearing receiving groove is provided inside the torque output mechanism, and a thrust needle roller bearing and at least two deep groove ball bearings are sequentially arranged in the bearing receiving groove. A bearing spacer is provided between the thrust needle roller bearing and the deep groove ball bearings. The outer ring of the thrust needle roller bearing is sleeved around the torque input mechanism and contacts the outer peripheral surface of the torque input mechanism. The first end of the bearing spacer contacts the inner ring of the thrust needle roller bearing, and the second end contacts the inner ring of the adjacent deep groove ball bearing. The outer ring of the deep groove ball bearing contacts the groove wall of the bearing receiving groove.

Description

Technical Field

[0001] This utility model belongs to the field of mechanical transmission technology, and specifically relates to a torque limiter. Background Technology

[0002] Torque limiters are primarily used in mechanical transmission to transmit torque. They are often used in high-speed rotating mechanisms and rotating mechanisms with varying heavy loads to protect equipment and personnel safety and ensure stable operation when the transmission system is overloaded or subjected to abnormal loads. Ball-type torque limiters are a commonly used type. They use a preset disc spring pressure to keep the balls engaged with slots on a flange. When the transmitted torque exceeds a set threshold, the balls disengage from the flange slots, cutting off power transmission and preventing damage to components. Once the overload is eliminated, they automatically reset and resume torque transmission. Existing ball-type torque limiters typically use single deep groove ball bearings. However, single deep groove ball bearings have insufficient axial load-bearing capacity, easily leading to poor dynamic stability and axial runout and radial misalignment under high speeds or alternating loads. To improve the insufficient axial load-bearing capacity, non-standard custom-made thin disc springs are required, which involves long lead times, high costs, and other supply chain risks. Utility Model Content

[0003] The purpose of this invention is to provide a torque limiter that can enhance torsional resistance and improve the stability of mechanism operation.

[0004] To achieve the above objectives, the present invention adopts the following technical solution:

[0005] A torque limiter includes: a torque input mechanism, a torque output mechanism, balls, and a torque adjustment component. The torque output mechanism is sleeved on the second end of the torque input mechanism, and the torque adjustment component is disposed on the first end of the torque input mechanism. The outer peripheral wall of the torque input mechanism has a radially protruding toothed engagement portion, which is located outside the torque output mechanism. The outer peripheral wall of the toothed engagement portion has ball grooves arranged at circumferential intervals, and the balls are disposed in the ball grooves. The end face of the first end of the torque output mechanism has slots corresponding to the number of balls, and each slot can be aligned with a ball groove, with the balls partially accommodated in the slots. The torque output mechanism is provided with a bearing receiving groove, in which a thrust needle roller bearing and at least two deep groove ball bearings are sequentially arranged. The thrust needle roller bearing is located on the side near the first end of the torque output mechanism. A flared bearing spacer is provided between the thrust needle roller bearing and the deep groove ball bearing. The outer ring of the thrust needle roller bearing is fitted around the periphery of the torque input mechanism and contacts the outer circumferential surface of the torque input mechanism. The first end of the bearing spacer contacts the inner ring of the thrust needle roller bearing, the second end of the bearing spacer contacts the inner ring of the adjacent deep groove ball bearing, and the outer ring of the deep groove ball bearing contacts the groove wall of the bearing receiving groove.

[0006] In some embodiments, the torque adjustment assembly includes an adjusting nut, a disc spring, and a spring frame sequentially fitted onto the torque input mechanism. The spring frame and the toothed engagement portion are arranged adjacent to each other and press against the ball bearing. The disc spring provides the spring frame with a force that presses the spring frame against the torque output mechanism.

[0007] In some embodiments, the torque adjustment assembly further includes an adjustment disk located between the disc spring and the adjustment nut, the adjustment nut pressing on the adjustment disk, and the adjustment disk pressing on the disc spring; the adjustment disk is provided with torque adjustment holes evenly spaced along a first pitch circle, and the adjustment nut is provided with positioning holes spaced along a second pitch circle, the diameters of the first and second pitch circles being equal, the number of positioning holes being less than the number of torque adjustment holes, and when the adjustment nut is rotated, at most one positioning hole can align with one torque adjustment hole on the adjustment disk.

[0008] In some embodiments, the interval angle α between adjacent torque adjusting holes on the adjusting disc and the minimum interval angle θ between adjacent positioning holes on the adjusting nut satisfy the following relationship:

[0009] α = 360 / n, where n is the number of torque adjustment holes on the adjustment disc;

[0010] θ = (k + 1 / m) × α, where k is an integer and m is the number of positioning holes on the adjusting nut.

[0011] In some embodiments, the outer peripheral wall of the torque input mechanism is provided with a limiting groove extending parallel to the axial direction of the torque input mechanism, and the inner ring wall of the adjusting disk is provided with a radially protruding rib. The rib and the limiting groove cooperate to restrict the rotation of the adjusting disk relative to the torque input mechanism.

[0012] In some embodiments, the slots are arranged at non-uniform intervals along the circumference on the end face of the first end of the torque output mechanism.

[0013] In some embodiments, the end face of the second end of the torque output mechanism is provided with a bearing fixing member, the bearing fixing member including a fixing disc fixed to the torque output mechanism and a bearing locking ring fixed to the torque input mechanism.

[0014] In some embodiments, the fixing disk is an annular plate, the outer ring diameter of the fixing disk is larger than the diameter of the bearing receiving groove, the inner ring diameter of the fixing disk is larger than the diameter of the inner ring of the deep groove ball bearing, and the fixing disk is fixed to the torque output mechanism by threaded fasteners.

[0015] In some embodiments, the outer ring diameter of the bearing locking ring is smaller than the inner ring diameter of the fixed disc, but larger than the inner ring diameter of the deep groove ball bearing, and the bearing locking ring is fixed to the torque input mechanism by threaded fasteners.

[0016] In some embodiments, the thrust needle roller bearing and the deep groove ball bearing are located entirely inside the torque output mechanism.

[0017] As can be seen from the above technical solution, this utility model combines a thrust needle roller bearing and at least two deep groove ball bearings. The thrust needle roller bearing mainly bears the axial load, while the deep groove ball bearing mainly bears the radial load. The combined load provides synergistic support, forming an axial-radial load splitting mechanism, enhancing dynamic stiffness, improving axial and radial torsional resistance, ensuring the stability of the mechanism's operation, and achieving performance and lifespan improvements. In the preferred embodiment, the adjusting nut and adjusting disc in the torque adjustment assembly are based on remainder modulation indexing coupling technology. Through mathematical constraints, a precise mechanical adjustment relationship is constructed, effectively solving the problem of insufficient precision in traditional equal-pitch adjustment. Attached Figure Description

[0018] To more clearly illustrate the embodiments of this utility model, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the torque limiter according to an embodiment of the present invention;

[0020] Figure 2 This is a cross-sectional view of the torque limiter according to an embodiment of the present invention;

[0021] Figure 3 This is a top view of the torque limiter according to an embodiment of the present invention;

[0022] Figure 4 This is a bottom view of the torque limiter according to an embodiment of the present invention;

[0023] Figure 5 This is a schematic diagram showing the cooperation between the torque input mechanism and the ball bearings in an embodiment of this utility model;

[0024] Figure 6 This is a schematic diagram showing the cooperation between the torque output mechanism and the ball bearings in an embodiment of this utility model;

[0025] Figure 7 This is a top view of the torque output mechanism according to an embodiment of the present invention;

[0026] Figure 8 This is a schematic diagram of the bearing locking ring according to an embodiment of the present invention;

[0027] Figure 9 This is a schematic diagram of the structure of the adjusting disc in an embodiment of the present invention;

[0028] Figure 10 This is a schematic diagram of the structure of the adjusting nut in an embodiment of this utility model.

[0029] The specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings. Detailed Implementation

[0030] The present invention will now be described in detail with reference to the accompanying drawings. In the detailed description of the embodiments of the present invention, for ease of explanation, the drawings illustrating the device structure will be partially enlarged without adhering to the general scale. Furthermore, the schematic diagrams are merely examples and should not limit the scope of protection of the present invention. It should be noted that the drawings are in a simplified form and use non-precise scales, solely for the purpose of conveniently and clearly illustrating the embodiments of the present invention. Additionally, in the description of this application, terms such as "first" and "second" are used only to distinguish descriptions and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Terms such as "positive," "negative," "bottom," "upper," "lower," "front," "rear," "left," and "right" indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention.

[0031] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" 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; they can also refer to the internal connection of two components; and they can refer to a wireless connection or a wired connection. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0032] Reference Figure 1 , Figure 2 , Figure 3 and Figure 4 The torque limiter in this embodiment includes a torque input mechanism 1, a torque output mechanism 2, a thrust needle roller bearing 3, a deep groove ball bearing 4, a bearing spacer 5, a ball bearing 6, a disc spring 7, an adjusting nut 8, and a spring frame 9.

[0033] In this embodiment, the torque input mechanism 1 is used to connect to the power output component and serves as the power input end of the torque limiter. In some embodiments, the power output component may be a drive component such as a motor, and the torque input mechanism 1 is equivalent to a bushing. The torque input mechanism 1 has a shaft hole extending along its own axial direction, and the motor output shaft (not shown) extends into the shaft hole of the torque input mechanism 1, driving the torque input mechanism 1 to rotate around its own axis. Specifically, a keyway 1b can be machined in the shaft hole 1a, and the motor output shaft and the torque input mechanism 1 are assembled together by the keyway 1b cooperating with the protrusion on the motor output shaft.

[0034] The torque output mechanism 2 serves as the output end of the torque limiter and is connected to the rotating component. The power output from the power output component is transmitted to the rotating component via the torque limiter, causing the rotating component to rotate. In this embodiment, the torque output mechanism 2 is a flange with threaded holes 2a machined on it. The flange is connected to the rotating component through the engagement of screws and threaded holes.

[0035] In this embodiment, the torque output mechanism 2 has a through hole (not labeled) extending along its own axial direction. One end of the torque input mechanism 1 is disposed within the through hole of the torque output mechanism 2, and the other end extends out of the through hole. For ease of explanation, the end of the torque input mechanism 1 extending out of the torque output mechanism 2 is defined as the first end, and the end of the torque input mechanism 1 located within the torque output mechanism 2 is defined as the second end. The first end of the torque output mechanism 2 and the first end of the torque input mechanism 1 are located on the same side, and the second end of the torque output mechanism 2 and the second end of the torque input mechanism 1 are also located on the same side.

[0036] The torque output mechanism 2 has an annular bearing receiving groove 2b that communicates with a through hole. A thrust needle roller bearing 3 and a deep groove ball bearing 4 are sequentially arranged within the bearing receiving groove 2b and fitted around the torque input mechanism 1 located within the through hole. The thrust needle roller bearing 3 is located on the side closer to the first end of the torque output mechanism 2, and the deep groove ball bearing 4 is located on the side closer to the second end of the torque output mechanism 2. A bearing spacer 5 is located between the thrust needle roller bearing 3 and the deep groove ball bearing 4. In this embodiment, the bearing receiving groove is machined within the torque output mechanism 2, completely enclosing the bearing inside the torque output mechanism 2, improving sealing, preventing dust ingress, and extending service life.

[0037] In this embodiment, the thrust needle roller bearing 3 primarily bears axial loads, enabling the entire mechanism to withstand greater axial loads, enhancing impact resistance, and its compact design reduces shaft movement. At least two deep groove ball bearings 4 are provided. These bearings primarily bear radial loads, providing radial support and ensuring high-speed rotational accuracy. Increasing the number of deep groove ball bearings 4 (at least two) improves the radial load-bearing capacity.

[0038] In this embodiment, both the thrust needle roller bearing 3 and the deep groove ball bearing 4 are standard products. For the specific structure of the thrust needle roller bearing, please refer to the IKO needle roller bearing selection manual. The thrust needle roller bearing 3 has an inner ring 3-1, an outer ring 3-2, and needle rollers 3-3 located between the inner ring 3-1 and the outer ring 3-2. According to the thrust needle roller bearing selection manual, the outer diameter of the outer ring is greater than the outer diameter of the inner ring, and the inner diameter of the outer ring is greater than the inner diameter of the inner ring. The outer ring 3-2 of the thrust needle roller bearing 3 is fitted around the torque input mechanism 1 and contacts the outer circumferential surface of the torque input mechanism 1.

[0039] The bearing spacer 5 located between the thrust needle roller bearing 3 and the deep groove ball bearing 4 is larger at the top and smaller at the bottom (within). Figure 2 (Taking the direction shown as an example) The bearing spacer 5 is flared, with the end having a larger outer diameter being the first end and the end having a smaller outer diameter being the second end. The first end of the bearing spacer 5 contacts the inner ring of the thrust needle roller bearing 3, and the second end of the bearing spacer 5 contacts the inner ring of the deep groove ball bearing 4. The outer ring of the deep groove ball bearing 4 contacts the groove wall of the bearing receiving groove 2b of the torque output mechanism 2. Through the bearing spacer 5, the thrust needle roller bearing 3 and the deep groove ball bearing 4 are used in combination, providing synergistic support for the composite load and forming an axial-radial load splitting mechanism, thereby enhancing the torsional resistance of the mechanism.

[0040] Reference Figure 2 and Figure 5 A radially protruding toothed engagement portion 1c is provided on the outer peripheral wall of the torque input mechanism 1. In this embodiment, the toothed engagement portion 1c is annular and located outside the torque output mechanism 2. A ball groove 1d is machined on the outer peripheral wall of the toothed engagement portion 1c, arranged at circumferential intervals. The balls 6 can engage within the ball grooves 1d and can be driven by the torque input mechanism 1 to rotate together around the axial direction of the torque input mechanism 1.

[0041] like Figure 6 As shown, a slot 2b corresponding to the number of balls 6 is provided on the end face of the first end of the torque output mechanism 2, and the slots 2b are arranged at intervals along the circumference. The balls 6 can be partially accommodated in the slots 2b, so that when the balls 6 are driven by the torque input mechanism 1 to rotate with the torque input mechanism 1, they can further drive the torque output mechanism 2 to rotate through their cooperation with the slots 2b, thereby realizing the transmission of rotational force.

[0042] Adjusting nut 8, disc spring 7, and spring frame 9 are arranged sequentially to form a torque adjustment assembly. The torque adjustment assembly is fitted onto the first end of torque input mechanism 1. Gear engagement part 1c is located between spring frame 9 and torque output mechanism 2. Spring frame 9 presses against ball 6. Disc spring 7 provides spring frame 9 with a force that presses it against torque output mechanism 2. Under the pressing action of spring frame 9, ball 6 is positioned within ball groove 1d and slot 2b, realizing the transmission of rotational force.

[0043] The adjusting nut 8 presses against the disc spring 7. The pressure on the disc spring is adjusted by changing the downward turning distance of the adjusting nut 8. The pressure on the disc spring 7 determines the torque required for the ball bearings to disengage. Various torque specifications can be accommodated by replacing different disc springs.

[0044] The torque limiter operates as follows: when the set torque is exceeded, the ball bearing 6 disengages from the ball groove 1d and slot 2b, preventing the torque input mechanism 1 from driving the torque output mechanism 2 to rotate, thus stopping the transmission of rotational force. After the ball bearing 6 disengages, the spring frame 9 springs upward, and the corresponding sensor receives the signal, enabling the equipment to stop abruptly. The operating principle of this torque limiter is the same as that of a conventional torque limiter, and will not be elaborated upon here.

[0045] In some embodiments, a bearing retainer 11 is further included on the second end face of the torque output mechanism 2. The bearing retainer 11 is used to lock and fix the bearing. In this embodiment, the bearing retainer 11 includes a fixing disc 11-1 and a bearing locking ring 11-2. The fixing disc 11-1 is an annular plate. The outer ring diameter of the fixing disc 11-1 is larger than the diameter of the bearing receiving groove 2b, and the inner ring diameter of the fixing disc 11-1 is larger than the diameter of the inner ring of the deep groove ball bearing. The fixing disc 11-1 is fixed to the torque output mechanism 2 by screws.

[0046] like Figure 2 and Figure 8 As shown, a fixing hole 11-2a is machined on the bearing locking ring 11-2, and a corresponding threaded hole is machined on the end face of the first end of the torque input mechanism 1. The bearing locking ring 11-2 is fixed to the torque input mechanism 1 by the engagement of a screw passing through the fixing hole 11-2a and the threaded hole. The outer ring diameter of the bearing locking ring 11-2 is smaller than the inner ring diameter of the fixing plate 11-1, and the outer ring diameter of the bearing locking ring 11-2 is larger than the inner ring diameter of the deep groove ball bearing 4. The deep groove ball bearing is locked and fixed by the fixing plate 11-1 and the bearing locking ring 11-2, thereby enabling the mechanism to withstand a greater axial load.

[0047] The axial load transmission process in this embodiment is as follows: adjusting nut 8 → disc spring 7 → spring frame 9 → ball bearing 6 → torque output mechanism 2 → outer ring of thrust needle roller bearing 3 → inner ring of thrust needle roller bearing 3 → bearing spacer 5 → inner ring of deep groove ball bearing 4 → bearing locking ring 11-2. This utility model can improve the problems of weak axial load capacity, narrow torque adjustment range, and high-speed dynamic imbalance existing in ball-type torque limiters.

[0048] In this embodiment, the number of slots 2b on the torque output mechanism 2 corresponds to the number of balls 6, and the number of ball grooves 1d on the gear meshing part 1c is greater than the number of balls 6. That is, the number of slots 2b on the torque output mechanism 2 is less than the number of ball grooves 1d on the gear meshing part 1c. The slots 2b on the torque output mechanism 2 can always be aligned with a portion of the ball grooves 1d on the gear meshing part 1c; that is, each slot 2b has one aligned ball groove 1d. Optionally, in some embodiments, the slots 2b on the first end face of the torque output mechanism 2 are arranged in a non-uniformly spaced manner on the circumference, i.e., as shown... Figure 7 As shown, the torque output mechanism 2 has five slots 2b arranged circumferentially on its first end face. However, these slots 2b are not perfectly equidistant. In this embodiment, the interval angle between two slots is 40°, while the interval angle between the remaining slots and their adjacent slots is 80°. This non-equidistant arrangement (staggered distribution) ensures that when the torque limiter exceeds the limit and the ball 6 disengages from the slot 2b, the ball can only re-enter the slot it was in at the initial state after the entire torque limiter mechanism has fully reset, thus continuing the transmission of rotational force. Using a uniform circumferential arrangement of slots might result in the ball entering a slot other than its initial state before the mechanism has fully reset, affecting the mechanism's operation. For example, when the slots are uniformly arranged circumferentially, it cannot be guaranteed that the ball will enter a slot other than its initial state when the mechanism resets, leading to a difference in the relative angular position between the two mechanisms connected by the torque limiter compared to the initial state, affecting the initial phase angle of the externally connected mechanism. This embodiment, by using a non-uniform circumferential arrangement of slots, avoids this situation.

[0049] To address the issue of insufficient torque adjustment precision, as a preferred embodiment, the torque adjustment assembly of this embodiment further includes an adjustment disc 10. The adjustment disc 10 is fitted onto the first end of the torque input mechanism 1, located between the disc spring 7 and the adjusting nut 8. The adjustment disc 10 is located on the side of the disc spring 7 furthest from the torque output mechanism 2 and can be connected to the disc spring 7 via screws and the rotating nut 8. When adjusting the disc spring pressure, turning the adjusting nut 8 downwards will cause the adjustment disc 10 to press the disc spring 7 downwards, thereby adjusting the downward pressure of the disc spring 7.

[0050] This embodiment achieves fine-tuned torque adjustment based on the principle of non-integer multiple indexing coupling. For example... Figure 9 and Figure 10 As shown, the adjusting disc 10 in this embodiment is provided with torque adjusting holes 10a evenly spaced along the first pitch circle A. The adjusting nut 8 is provided with positioning holes 8a spaced along the second pitch circle B. The diameters of the first pitch circle A and the second pitch circle B are equal. The number of positioning holes 8a is less than the number of torque adjusting holes 10a, and when the adjusting nut 8 is rotated, at most one positioning hole 8a on the adjusting nut 8 can align with the torque adjusting hole 10a on the adjusting disc 10. The positioning holes are used to further subdivide the adjustment range (basic adjustment angle) of the torque adjusting holes.

[0051] Furthermore, the interval angle α between adjacent torque adjustment holes 10a on the adjusting disc 10, and the minimum interval angle θ between adjacent positioning holes 8a on the adjusting nut 8, satisfy the following relationship:

[0052] α = 360 / n, where n is the number of torque adjustment holes on the adjustment disc;

[0053] θ = (k + 1 / m) × α, where k and m are integers, and m is the number of positioning holes on the adjusting nut.

[0054] Taking this embodiment as an example, there are 20 torque adjustment holes 10a on the adjusting disc 10, i.e., n = 20, and the interval angle α between adjacent torque adjustment holes 10a is 360 / 20 = 18°. The adjusting nut 8 has 3 positioning holes 8a, i.e., m = 3. Let k = 5, and the minimum interval angle θ between adjacent positioning holes 8a on the adjusting nut 8 is (5 + 1 / 3) × 18 = 96°. When the adjusting nut 8 rotates 6°, one positioning hole 10a on the adjusting nut 8 aligns with one torque adjustment hole 8a on the adjusting disc 10. This further subdivides the torque adjustment holes on the adjusting disc 10 into three equal parts, thereby achieving more precise torque adjustment.

[0055] In this embodiment, the adjusting nut is used in conjunction with the adjusting disc. By dividing the basic adjusting angle α into m equal parts, the original n-level adjusting range is expanded to n·m levels, which achieves a geometrical improvement in torque adjustment resolution and can solve the problem of insufficient adjustment precision caused by the cumulative error of gaps in the hole positions.

[0056] In some embodiments, optionally, to prevent the adjusting disk 10 from rotating relative to the torque input mechanism 1, the adjusting disk 10 and the torque input mechanism 1 are fitted together by a keyway structure. A limiting groove 1e extending parallel to the axial direction of the torque input mechanism 1 is machined on the outer peripheral wall of the torque input mechanism 1, and a radially protruding rib 10b is machined on the inner annular wall of the adjusting disk 10. The rib 10b can cooperate with the limiting groove 1e, thereby limiting the rotation of the adjusting disk 10 relative to the torque input mechanism 1, but not limiting the movement of the adjusting disk 10 along the axial direction of the torque input mechanism 1.

[0057] The above description of the disclosed embodiments enables those skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. Torque limiter, including: A torque input mechanism, a torque output mechanism, a ball bearing, and a torque adjustment component are provided, wherein the torque output mechanism is sleeved on the second end of the torque input mechanism, and the torque adjustment component is disposed on the first end of the torque input mechanism; characterized in that: The outer peripheral wall of the torque input mechanism is provided with a radially protruding toothed meshing part, the toothed meshing part is located outside the torque output mechanism, and the outer peripheral wall of the toothed meshing part is provided with ball grooves arranged at intervals along the circumference, the balls being disposed in the ball grooves. The first end of the torque output mechanism has a slot on its end face corresponding to the number of balls. Each slot can be aligned with a ball groove, and the balls are partially accommodated in the slot. The torque output mechanism has a bearing receiving groove, in which a thrust needle roller bearing and at least two deep groove ball bearings are arranged in sequence. The thrust needle roller bearing is located on the side closer to the first end of the torque output mechanism. A flared bearing spacer is provided between the thrust needle roller bearing and the deep groove ball bearing. The outer ring of the thrust needle roller bearing is fitted around the torque input mechanism and contacts the outer peripheral surface of the torque input mechanism. The first end of the bearing spacer contacts the inner ring of the thrust needle roller bearing. The second end of the bearing spacer contacts the inner ring of the adjacent deep groove ball bearing. The outer ring of the deep groove ball bearing contacts the groove wall of the bearing receiving groove.

2. The torque limiter as described in claim 1, characterized in that: The torque adjustment assembly includes an adjusting nut, a disc spring, and a spring frame sequentially fitted onto the torque input mechanism. The spring frame and the toothed engagement portion are arranged adjacent to each other and press against the ball bearing. The disc spring provides the spring frame with a force that causes the spring frame to press against the torque output mechanism.

3. The torque limiter as described in claim 2, characterized in that: The torque adjustment assembly further includes an adjustment disc, which is located between the disc spring and the adjustment nut, with the adjustment nut pressing on the adjustment disc and the adjustment disc pressing on the disc spring; The adjusting plate is provided with torque adjusting holes evenly spaced along the first pitch circle, and the adjusting nut is provided with positioning holes spaced along the second pitch circle. The diameters of the first and second pitch circles are equal. The number of positioning holes is less than the number of torque adjusting holes, and when the adjusting nut is rotated, at most only one positioning hole can be aligned with one torque adjusting hole on the adjusting plate.

4. The torque limiter as described in claim 3, characterized in that: The interval angle α between adjacent torque adjustment holes on the adjustment disc and the minimum interval angle θ between adjacent positioning holes on the adjustment nut satisfy the following relationship: α = 360 / n, where n is the number of torque adjustment holes on the adjustment disc; θ = (k + 1 / m) × α, where k is an integer and m is the number of positioning holes on the adjusting nut.

5. The torque limiter as described in claim 3, characterized in that: The outer peripheral wall of the torque input mechanism is provided with a limiting groove extending parallel to the axial direction of the torque input mechanism, and the inner ring wall of the adjusting disk is provided with a radially protruding rib. The rib and the limiting groove cooperate to restrict the rotation of the adjusting disk relative to the torque input mechanism.

6. The torque limiter as described in claim 1, characterized in that: The slots are arranged at non-uniform intervals along the circumference on the end face of the first end of the torque output mechanism.

7. The torque limiter as described in claim 1, characterized in that: The second end of the torque output mechanism is provided with a bearing fixing component, which includes a fixing disc fixed to the torque output mechanism and a bearing locking ring fixed to the torque input mechanism.

8. The torque limiter as described in claim 7, characterized in that: The fixed disk is a circular annular plate. The outer ring diameter of the fixed disk is larger than the diameter of the bearing receiving groove, and the inner ring diameter of the fixed disk is larger than the diameter of the inner ring of the deep groove ball bearing. The fixed disk is fixed to the torque output mechanism by threaded fasteners.

9. The torque limiter as described in claim 8, characterized in that: The outer ring diameter of the bearing locking ring is smaller than the inner ring diameter of the fixed disc, but larger than the inner ring diameter of the deep groove ball bearing. The bearing locking ring is fixed to the torque input mechanism by threaded fasteners.

10. The torque limiter as claimed in claim 1, characterized in that: The thrust needle roller bearing and the deep groove ball bearing are located entirely inside the torque output mechanism.

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