Torque limiter, transmission components and piping system

Abstract

This invention discloses a torque limiter, a transmission assembly, and a piping system, including: a torque input assembly and a torque output assembly; the torque input assembly includes a drive shaft configured to rotate in a controlled manner about a rotation axis; the torque output assembly includes a sleeve, an elastic element, and a transmission shaft disposed along the rotation axis, the elastic element having a first end and a second end; wherein, the first end is configured to generate a maximum static friction torque through frictional transmission between the sleeve and the drive shaft, and when the rotational torque of the drive shaft exceeds the maximum static friction torque, the drive shaft rotates relative to the sleeve to interrupt torque transmission; the second end is configured to deform with the movement of the transmission shaft along the rotation axis and accumulate a rebound force to drive the transmission shaft back to its original position. This invention solves the technical problems of low efficiency and unstable torque in manual operation.

Description

Technical Field

[0001] This invention relates to the field of pipeline control technology for transfer tank trucks, specifically to torque limiters, transmission components, and pipeline systems. Background Technology

[0002] As a critical rocket-to-ground interface, the pressure relief valve of the rocket's gas supply connector is of paramount importance in terms of the reliability and safety of its opening and closing operation. Currently, it is still mainly operated manually, which has obvious shortcomings: First, it involves multiple tools and operating methods, resulting in low efficiency and posing an explosion risk in flammable and explosive propellant environments; second, the torque applied manually is unstable, easily damaging components such as the valve stem and sealing surfaces due to overload, and lacks the ability to interrupt torque in a timely manner and automatically reset. Summary of the Invention

[0003] In view of the shortcomings of the existing technology, the purpose of this invention is to provide a torque limiter, transmission components and piping system to solve the technical problems of low efficiency and unstable torque in manual operation.

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

[0005] On the one hand, a torque limiter is provided, including:

[0006] A torque input assembly includes a drive shaft configured to rotate in a controlled manner about a rotation axis;

[0007] A torque output assembly includes a sleeve, an elastic element, and a drive shaft arranged along the rotation axis, the elastic element having a first end and a second end;

[0008] The first end is configured to have a maximum static friction torque due to frictional transmission between the sleeve and the drive shaft. When the rotational torque of the drive shaft is greater than the maximum static friction torque, the drive shaft rotates relative to the sleeve and interrupts the torque transmission. The second end is configured to deform as the drive shaft moves along the rotation axis and accumulate a rebound force to drive the drive shaft to reset.

[0009] In one embodiment, the drive shaft has a first connecting section extending along the rotation axis, and the circumferential surface of the first connecting section is provided with at least one edge.

[0010] In one embodiment, the drive shaft has a second connecting section, the second connecting section being provided with an adjusting member configured to move in a controlled manner relative to the second connecting section to abut against the second end and to adjust the maximum static friction torque.

[0011] In one embodiment, the first connecting segment and the second connecting segment are coaxial and detachably connected.

[0012] In one embodiment, the adjusting member is a preload screw threaded to the second connecting section.

[0013] In one embodiment, the sleeve includes an inner tube and an outer tube that are slidably sleeved along the rotation axis, the inner tube being driven by friction with the drive shaft, and a receiving cavity is formed between the inner tube and the outer tube to accommodate the elastic element.

[0014] In one embodiment, the elastic element is a spring.

[0015] In one embodiment, the torque input assembly further includes a servo motor for driving the drive shaft to rotate, as well as a mounting plate and a mounting base. The mounting plate supports the servo motor and is slidably connected to the mounting base, which has a fastener for fixing the mounting plate.

[0016] In another aspect, a transmission assembly is provided, including a reducer, a thruster, and the torque limiter described above. The reducer includes a meshing first gear and a second gear, and the thruster is used to push or pull the torque limiter and to drive or disconnect the transmission shaft from the first gear.

[0017] In another aspect, a piping system is also provided, including a pressure relief valve and the aforementioned transmission assembly, wherein the pressure relief valve is connected to the second gear transmission for opening and closing the pressure relief valve.

[0018] Compared with existing technologies, the present invention has the following advantages: the maximum static friction torque can be precisely set through friction transmission between the drive shaft and the sleeve. When the input torque exceeds the threshold, the drive shaft and the sleeve rotate relative to each other, interrupting the transmission of torque to the output side. This not only enables automatic opening and closing of the pressure relief valve, improving efficiency, but also avoids component damage due to overload, improving the stability and reliability of the pressure relief valve's opening and closing. At the same time, during the docking process, when the drive shaft is subjected to axial thrust, the second end of the elastic element is compressed and deformed. On the one hand, the docking impact energy is converted into elastic potential energy to reduce the damage of instantaneous impact to various components. On the other hand, the accumulated rebound force keeps the drive shaft in a tight state, ensuring docking in place and the continuity and stability of torque transmission. Attached Figure Description

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

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

[0021] Figure 3 This is a cross-sectional view of a torque output component according to an embodiment of the present invention;

[0022] Figure 4 This is a partial cross-sectional view of a transmission assembly according to an embodiment of the present invention;

[0023] Figure 5 This is a schematic diagram of the reducer and pressure relief valve according to an embodiment of the present invention.

[0024] The reference numerals in the accompanying drawings include:

[0025] 1. Drive shaft; 101. Servo motor; 102. Mounting plate; 103. Mounting base; 104. Fixture;

[0026] 2. Sleeve; 201. Inner tube; 202. Outer tube;

[0027] 3. Elastic element; 301. First end; 302. Second end;

[0028] 4. Drive shaft; 401. First connecting section; 402. Second connecting section;

[0029] 5. Adjusting components;

[0030] 6. Reducer; 601. First gear; 602. Second gear;

[0031] 7. Pressure relief valve;

[0032] X, axis of rotation. Detailed Implementation

[0033] The present invention will be further described in detail below through specific embodiments:

[0034] In embodiments of the present invention, such as Figures 1-3 As shown, the torque limiter includes a torque input component and a torque output component; the torque input component includes a drive shaft 1 configured to rotate in a controlled manner about a rotation axis X; the torque output component includes a sleeve 2, an elastic element 3 and a transmission shaft 4 disposed along the rotation axis X, the elastic element 3 having a first end 301 and a second end 302;

[0035] The first end 301 is configured to have a maximum static friction torque so that the sleeve 2 and the drive shaft 1 are in frictional transmission. When the rotational torque of the drive shaft 1 is greater than the maximum static friction torque, the drive shaft 1 rotates relative to the sleeve 2 and interrupts the torque transmission. The second end 302 is configured to deform as the drive shaft 4 moves along the rotation axis X and accumulate a rebound force to drive the drive shaft 4 to reset.

[0036] Specifically, in this embodiment of the invention, the torque limiter includes a torque input component and a torque output component. The torque input component provides power, which is transmitted and output through the torque output component. Specifically, the torque input component includes a drive shaft 1, which forms a rotation axis X along its axis. Under the action of an external force, the drive shaft 1 can rotate around the rotation axis X.

[0037] In this embodiment of the invention, the torque output assembly includes a sleeve 2, an elastic element 3, and a drive shaft 4, all coaxially arranged along the rotation axis X. For example... Figure 2 , Figure 3 As shown, the elastic element 3 serves as an intermediate connecting component, forming the first end 301 of the connecting sleeve 2 and the second end 302 of the connecting drive shaft 4. The sleeve 2 is used to connect the drive shaft 1, allowing the drive shaft 4 to transmit torque. Thus, by using this torque limiter in the opening and closing of the pressure relief valve, manual operation can be replaced. This avoids the inhalation hazard to workers caused by the volatilization of residual toxic liquid in the transfer pipeline during withdrawal, and also reduces the operational risks of manual work in an explosion-proof environment. Furthermore, it improves the operational efficiency of propellant transfer and reduces the difficulty of manual work involving different tools and operating procedures.

[0038] In addition, to improve the stability and reliability of the pressure relief valve's opening and closing, the first end 301 of the elastic element 3 abuts against the sleeve 2, and a preload force acting axially is generated through the pre-compression of the elastic element 3. This preload force presses the friction surface of the sleeve 2 against the corresponding friction surface of the drive shaft 1, thereby forming a friction transmission pair between the sleeve 2 and the drive shaft 1. By considering the friction coefficient, contact area, and the magnitude of the preload force provided by the elastic element 3, the maximum static friction torque that the friction transmission pair can transmit can be precisely set. Specifically, the maximum static friction torque M... max =μ×F N ×r eq Where μ is the coefficient of friction, F N The positive pressure generated by the preload of elastic element 3, r eq The effective radius of friction is denoted as .

[0039] When drive shaft 1 rotates under normal operating conditions, its rotational torque is less than or equal to the maximum static friction torque. At this time, there is no relative rotation between drive shaft 1 and sleeve 2. Drive shaft 1 drives sleeve 2 to rotate synchronously through frictional torque, thereby driving the subsequent transmission shaft 4 and pressure relief valve. When the rotational torque of drive shaft 1 unexpectedly increases and exceeds the maximum static friction torque, the static friction state between drive shaft 1 and sleeve 2 is disrupted, and they slide relative to each other. This causes drive shaft 1 to spin freely relative to sleeve 2 and cannot continue to transmit effective torque to sleeve 2, thus instantly interrupting the transmission of torque to the output side (i.e., transmission shaft 4), preventing damage to vulnerable components due to excessive torque. In actual operation, for example, using a torque of approximately 1 Nm, rotating 4-5 revolutions is sufficient to fully open the valve, and the entire process is completed in 5 seconds. This improves the operational efficiency of propellant transfer and reduces the difficulty of manual operation involving different tools and operating procedures. Conversely, it will automatically slip in case of overload, such as limiting the maximum torque to 2.5 Nm, thereby preventing excessive torque from damaging the pressure relief valve. This avoids the risk of propellant leakage caused by component damage due to unstable torque during manual operation, and also extends the service life of the pressure relief valve in stable torque operating environments.

[0040] Furthermore, to ensure that the drive shaft 1 and sleeve 2 do not stick together due to frictional heat after slippage, a wear-resistant coating can be applied to their friction contact surfaces or different metal materials can be used for pairing. When the overload is released, the rotational torque of the drive shaft 1 returns to below the threshold, the friction transmission pair automatically returns to the static friction state, and the drive shaft 1 drives the sleeve 2 to rotate again without manual reset.

[0041] The second end face of the elastic element 3 is connected to or abuts against the drive shaft 4, and the elastic element 3 is arranged along the rotation axis X. When the drive shaft 4 moves axially along the rotation axis X under the action of an external force (e.g., during the docking process, the drive shaft 4 is subjected to an axial thrust from the docking end), the second end 302 of the elastic element 3 is compressed, thereby generating elastic deformation. This deformation process converts the axial impact energy of the external environment into elastic potential energy, playing a role in buffering and absorbing energy; on the other hand, the deformed elastic element 3 will accumulate a rebound force proportional to the deformation, which always acts on the drive shaft 4 in the opposite direction to the external force.

[0042] Specifically, when the drive shaft 4 is axially pushed by the docking end (in a state where it is not fully docked), the second end 302 of the elastic element 3 is compressed, absorbing the impact energy of docking during deformation, thus preventing damage to the drive shaft 4 and other components from rigid collisions. At the same time, the rebound force accumulated by the elastic element 3 continuously pushes the drive shaft 4 against the docking end in the opposite direction, ensuring reliable contact between the drive shaft 4 and the docking end. This prevents the drive shaft 4 from disengaging due to vibration or slight displacement during torque transmission, and allows the torque to be stably transmitted from the drive shaft 4 to the docking end, ensuring the continuity and reliability of the pressure relief valve's opening and closing action.

[0043] During the docking operation, if the drive shaft 4 has not yet fully moved to the predetermined working position (for example, due to guide deviation, mechanical jamming, or initial clearance), the rebound force accumulated by the elastic element 3 will automatically push the drive shaft 4 to move in the correct direction along the rotation axis X until the drive shaft 4 forms stable contact with the docking end. This process requires no external intervention or additional reset drive mechanism, achieving automatic compensation of the docking position.

[0044] In this embodiment, the elastic element 3 enables frictional transmission between the sleeve 2 and the drive shaft 1, and forms overload protection in case of overload, ensuring the stability and safety of the pressure relief valve opening and closing. At the same time, the elastic element 3 can also absorb and automatically compensate for the thrust acting on the drive shaft 4, so as to complete the automatic docking of the drive shaft 4. In this process, the rigid docking is transformed into a flexible docking, which improves the stability of the docking process and thus increases the reliability of the pressure relief valve opening and closing.

[0045] Specifically, the first end 301 of the elastic element 3 presses the sleeve 2 against the drive shaft 1 through the preload of the elastic element 3 to form a friction transmission pair, and the maximum static friction torque can be set. When the rotational torque of the drive shaft 1 exceeds this threshold, the drive shaft 1 and the sleeve 2 slide relative to each other, interrupting the torque transmission. After the overload is released, the friction pair automatically recovers. The second end 302 of the elastic element 3 is connected to the drive shaft 4. When the drive shaft 4 moves under axial thrust, the elastic element 3 deforms to absorb the impact energy and accumulates the rebound force. This rebound force, on the one hand, keeps the drive shaft 4 pressed against the docking end to maintain reliable force transmission, and on the other hand, automatically compensates for the position deviation and pushes it to the correct working position when the drive shaft 4 is not in place. With the coordinated work of its first end 301 and second end 302, multiple purposes such as overload protection, docking buffer, pressing and holding, and automatic position compensation are achieved. The structure is simple and can ensure the stability and reliability of the opening and closing of the pressure relief valve.

[0046] like Figures 1-3As shown, in one embodiment, the drive shaft 4 has a first connecting segment 401 extending along the rotation axis X, and the circumferential surface of the first connecting segment 401 is provided with at least one edge. Specifically, the edge refers to a straight edge that protrudes radially outward or recesses radially from the surface of the first connecting segment 401, and the edge extends continuously or discontinuously in a direction parallel to the rotation axis X. Thus, by providing the edge, the cross-section of the first connecting segment 401 is non-circular, such as triangular, rectangular, hexagonal, spline-shaped, or with a single keyway.

[0047] The first connecting section 401 and its edges are designed to mate with a matching hole or slot on an external driven element. This matching hole has the same non-circular profile as the first connecting section 401. When the drive shaft 4 rotates, the edges and the corresponding surfaces of the matching hole form normal contact, thereby transmitting torque to the external element. Simultaneously, since the edges only restrict relative rotation and not axial movement, the drive shaft 4 can slide freely within the matching hole along the rotation axis X, facilitating axial deformation or reset of the second end 302 of the elastic element 3.

[0048] In a preferred embodiment, the first connecting segment 401 has a regular hexagonal cross-section, with six edges naturally formed on its circumference. The regular hexagonal cross-section has the advantages of simple processing, good alignment, and low stress concentration. The matching hexagonal hole allows the drive shaft 4 to slide smoothly after insertion, while also eliminating any backlash.

[0049] In another embodiment, the circumferential surface of the first connecting segment 401 has only one edge, specifically manifested as an axially extending flat key structure. For example, a flat surface is milled into the cylindrical surface of the first connecting segment 401 to form an edge. A hole with a corresponding flat surface is provided on the mating part, which can also realize unidirectional torque transmission. The single-edge structure is suitable for applications with smaller transmitted torque and has lower cost. Of course, the mating hole or groove can be fitted with a copper alloy bushing or have a surface lubricating coating (such as molybdenum disulfide) to reduce sliding friction and ensure the smoothness of the drive shaft 4 during axial movement.

[0050] When the drive shaft 4 is subjected to axial thrust from the mating end, the edge of the first connecting section 401 slides within the matching hole, while the second end 302 of the elastic element 3 is compressed and accumulates rebound force. Since the edge always maintains the geometric constraint for torque transmission, the rotational torque of the drive shaft 1 can be ultimately transmitted to the external load through the sleeve 2, the elastic element 3, and the drive shaft 4, thus realizing the opening and closing action of the pressure relief valve. When the mating impact is too large or a positional deviation occurs, the sliding guiding effect of the edge ensures that the drive shaft 4 moves in a straight line, avoiding jamming, while the rebound force of the elastic element 3 pushes the drive shaft 4 to precisely reset.

[0051] like Figure 2 , Figure 3As shown, in one embodiment, the drive shaft 4 has a second connecting section 402, which is provided with an adjusting member 5. The adjusting member 5 is configured to move controllably relative to the second connecting section 402 to abut against the second end 302 and to adjust the maximum static friction torque. Specifically, the adjusting member 5 is used to directly abut against the second end 302 of the elastic member 3. When the adjusting member 5 moves on the second connecting section 402, it changes the initial compression of the elastic member 3, thereby changing the preload applied by the elastic member 3 to the drive shaft 4 and the friction pair. Since the maximum static friction torque of the first end 301 that causes the sleeve 2 to frictionally drive the drive shaft 1 directly depends on the normal pressure provided by the elastic member 3, the set value of the maximum static friction torque can be adjusted by changing the deformation of the elastic member 3 by moving the adjusting member 5.

[0052] In a preferred embodiment, the second connecting segment 402 is provided with external threads, and the adjusting member 5 is an annular nut with matching internal threads on its inner circumferential surface. The second end 302 of the elastic member 3 is fitted onto the second connecting segment 402 and abuts against one side end face of the adjusting member 5. The operator uses a wrench or special tool to rotate the annular nut, causing it to move axially along the second connecting segment 402: when the nut is screwed in towards the elastic member 3, the elastic member 3 is further compressed, the elastic force increases, the positive pressure between the sleeve 2 and the drive shaft 1 increases, and the maximum static friction torque increases accordingly; when the nut is screwed out in the opposite direction, the spring compression decreases, and the maximum static friction torque decreases. After adjustment, the thread friction between the nut and the second connecting segment 402 can achieve self-locking, or a locking nut can be added to prevent loosening.

[0053] As another embodiment, such as Figure 3 As shown, the adjusting member 5 is a preload screw and abuts against the second end 302 of the elastic member 3; the second connecting section 402 of the transmission shaft 4 is provided with an internal thread hole; the preload screw can be rotated in both directions.

[0054] For ease of use on-site, graduations or color markings can be marked on the outer circumference of the second connecting section 402 of the drive shaft 4 or on the adjusting component 5. For example, each graduation line corresponds to a maximum static friction torque value. Before leaving the factory or on the calibration fixture, the slippage torque corresponding to different adjustment positions can be calibrated using a torque sensor to create a reference table for operators. The movement range of the adjusting component 5 should ensure that the elastic component 3 is always within the elastic deformation range to avoid plastic deformation.

[0055] It should be noted that the adjusting component 5 only changes the preload of the elastic component 3, thereby adjusting the maximum static friction torque of the friction pair at the first end 301, but does not affect the original function of the second end 302. When the drive shaft 4 is subjected to axial thrust during docking, the elastic component 3 will still generate additional deformation to absorb the impact and accumulate rebound force. At this time, the adjusting component 5, as a movable contact surface, will move with the drive shaft 4 as a whole without interfering with the dynamic response of the elastic component 3. At the same time, the adjusting component 5 does not affect the torque transmission function of the edge on the first connecting section 401. The three components are independent of each other and together constitute an adjustable threshold, buffer reset, and sliding torque transmission integrated torque limiter.

[0056] Of course, the overload protection threshold required for different models of air supply connectors or the same connector under different operating conditions may vary. By setting this adjusting component 5, various requirements can be quickly adapted simply by rotating and adjusting with a simple tool, without replacing the elastic component 3 or other parts, greatly improving the versatility and field adaptability of this torque limiter. In addition, if the elastic component 3 experiences fatigue and loosening after long-term use, resulting in a decrease in slippage torque, it can also be recalibrated through the adjusting component 5, extending the service life of the device.

[0057] The first connecting segment 401 and the second connecting segment 402 are coaxial and detachably connected. Specifically, the first connecting segment 401 has a first connecting part at the end near the second connecting segment 402, and the second connecting segment 402 has a second connecting part at the end near the first connecting segment 401. The first connecting part and the second connecting part are detachably fixed by means of threaded connection, pin connection, snap-fit ​​connection or coupling connection, etc., and ensure that the coaxiality error of the two after assembly is within the allowable range.

[0058] In a preferred embodiment, the first connecting segment 401 has an internally threaded blind hole at its end center, and the second connecting segment 402 has a coaxial externally threaded post at its end. During assembly, the externally threaded post is screwed into the internally threaded blind hole until the end face of the second connecting segment 402 is tightly fitted with the end face of the first connecting segment 401, forming a rigid connection. To prevent the threads from loosening during rotation of the drive shaft 4 or axial impact, thread-locking adhesive can be applied to the threaded connection, or a radial locking screw can be installed to pass through the side wall of the first connecting segment 401 to press the externally threaded post of the second connecting segment 402.

[0059] In another embodiment, the first connecting segment 401 and the second connecting segment 402 are connected by a cylindrical pin or a tapered pin. Specifically, the end of the first connecting segment 401 is provided with a coaxial optical hole, and the end of the second connecting segment 402 is provided with a coaxial optical axis. The two are positioned by a transition fit, and then a pin hole is drilled radially and a cylindrical pin or a tapered pin is driven in. This is suitable for withstanding large torque and axial force, and disassembly only requires punching out the pin.

[0060] As another embodiment, to accommodate frequent disassembly and assembly, a splined sleeve connection can be used: the end of the first connecting section 401 is provided with an external spline, and the end of the second connecting section 402 is provided with an internal spline. After the two are inserted, their axial position is fixed by a quick-release clamp or a lock nut. This facilitates quick disassembly and assembly, requires no tools, and is suitable for on-site maintenance.

[0061] Furthermore, the first connecting section 401 requires at least one edge to be machined on its circumference, while the second connecting section 402 requires a threaded structure to accommodate the adjusting component 5. If both were made into a single long shaft, the overall machining process would be complex, resulting in significant material waste and a low yield. Separating them allows for optimal machining of each section before assembly, reducing manufacturing costs. Additionally, the adjusting component 5 needs to be mounted on the second connecting section 402; if the drive shaft 4 were a single piece, the adjusting component 5 could only be inserted from the shaft end, which might already have a non-circular cross-section of the first connecting section 401, preventing passage. The separate structure allows the adjusting component 5 to be installed on the second connecting section 402 first, followed by connecting the first connecting section 401 to the second connecting section 402, facilitating assembly. Moreover, when the adjusting component 5 and / or the first connecting section 401 wear out, only the corresponding component needs to be replaced, resulting in low maintenance costs.

[0062] The assembled drive shaft 4 has its first connecting section 401's edge engaging with the external driven element to transmit torque, while the adjusting piece 5 on its second connecting section 402 abuts against the second end 302 of the elastic member 3 to adjust the maximum static friction torque. The split structure does not alter the function of these two parts; instead, it allows for adjustable length dimensions between them, thus adapting to the installation space requirements of different pressure relief valves. Furthermore, during impact, the detachable connection between the first connecting section 401 and the second connecting section 402 must possess sufficient impact resistance.

[0063] As shown in the figure Figure 2 , Figure 3As shown, in one embodiment, the sleeve 2 includes an inner tube 201 and an outer tube 202 that are slidably fitted along the rotation axis X. The inner tube 201 is driven by friction with the drive shaft 1, and a receiving cavity is formed between the inner tube 201 and the outer tube 202 to accommodate the elastic element 3. Specifically, the outer tube 202 is fitted outside the inner tube 201, and the inner tube 201 and the outer tube 202 can slide relative to each other along the rotation axis X. To ensure smooth sliding and prevent jamming, a clearance fit is used between the outer cylindrical surface of the inner tube 201 and the inner cylindrical surface of the outer tube 202, and a lubricating coating or bushing can be provided to reduce the coefficient of friction. At the same time, to prevent relative rotation between the inner tube 201 and the outer tube 202 from affecting the stability of torque transmission, circumferential locking can be achieved between them through a sliding fit of splines, guide keys, or polygonal cross sections, which allows axial relative movement while restricting synchronous rotation. For example, a protruding guide key is provided on the outer peripheral surface of the inner tube 201 along the axial direction, and a corresponding keyway is opened on the inner peripheral surface of the outer tube 202; or the outer peripheral surface of the inner tube 201 is machined into a hexagon, and the inner hole of the outer tube 202 is machined into a matching hexagon.

[0064] When the inner tube 201 and the outer tube 202 are slidably fitted together, a closed or semi-closed space is formed between them, which is the receiving cavity. Specifically, the radial boundary of the receiving cavity is formed by the inner wall of the outer tube 202, and the axial boundary is jointly defined by one end face (or step) of the inner tube 201 and one end face (or step) of the outer tube 202. This receiving cavity is used to accommodate the elastic element 3.

[0065] The end of the inner tube 201 near the drive shaft 1 is configured to form a friction transmission pair with the drive shaft 1. The pre-compression force of the elastic element 3 presses the friction surface of the inner tube 201 against the friction surface of the drive shaft 1, thereby generating a preset maximum static friction torque. When the rotational torque of the drive shaft 1 exceeds this threshold, relative sliding occurs between the inner tube 201 and the drive shaft 1, interrupting the torque transmission.

[0066] The elastic element 3 is located within the receiving cavity, with its first end 301 abutting against the inner tube 201 and its second end 302 abutting against the adjusting element 5. Thus, the first end 301 of the elastic element 3 pushes the inner tube 201 against the drive shaft 1, providing frictional pressure; the second end 302 of the elastic element 3 bears the axial force from the drive shaft 4. When the drive shaft 4 is subjected to external axial thrust during docking and moves closer to the drive shaft 1, the drive shaft 4 pushes the second end 302 of the elastic element 3, further compressing the elastic element 3, increasing its deformation, and accumulating greater rebound force. This rebound force is transmitted to the inner tube 201 through the first end 301, increasing the positive pressure between the inner tube 201 and the drive shaft 1, thereby automatically raising the overload protection threshold in the docking tight state to prevent accidental slippage. On the other hand, it directly reacts to the drive shaft 4, ensuring it always maintains a tight grip on the docking end, guaranteeing the reliability of torque transmission.

[0067] In the aforementioned embodiment, an adjusting member 5 is provided on the second connecting section 402 of the drive shaft 4. This adjusting member 5 can extend into the receiving cavity and directly abut against the second end 302 of the elastic member 3. By rotating the adjusting member 5 to change its axial position on the second connecting section 402, the initial compression of the elastic member 3 can be adjusted, thereby precisely setting the initial maximum static friction torque between the inner tube 201 and the drive shaft 1. During the docking and pushing process, the adjusting member 5 moves along with the drive shaft 4, further compressing the elastic member 3. However, this dynamic compression is an additional deformation based on the initial setting and does not change the calibration relationship of the initial setting value.

[0068] Furthermore, the elastic element 3 is completely enclosed within the cavity between the inner tube 201 and the outer tube 202, eliminating the need for additional axial space and making the overall design more compact. This is advantageous for installation in space-constrained applications such as the rocket body gas supply connector. The sliding fit between the inner tube 201 and the outer tube 202 provides precise guidance for the compression of the elastic element 3 and the axial movement of the drive shaft 4, preventing bending or skewness of the elastic element 3 and ensuring a stable and reliable deformation process. Moreover, the cavity isolates the elastic element 3 from the external environment (such as propellant vapor, dust, ice crystals, etc.), reducing corrosion and contamination and extending the service life of the elastic element 3. In other embodiments, a sealing ring can be provided at the port of the outer tube 202 to provide a sliding seal with the drive shaft 4, further enhancing the protection level.

[0069] like Figure 2 , Figure 3 As shown, in one embodiment, the elastic element 3 is a spring. Specifically, the elastic element 3 can be a helical compression spring, a disc spring assembly, or a wave spring, with an inner diameter larger than the outer diameter of the inner tube 201 and an outer diameter smaller than the inner diameter of the outer tube 202, so that it can be freely placed in the receiving cavity and deformed axially. In this embodiment, taking a helical compression spring as an example, its initial pre-compression is calculated so that when the drive shaft 4 is unloaded (not docked), the spring applies a small preload to the drive shaft 4 through the second end 302, keeping the drive shaft 4 at the initial limit position; during the docking and pushing process, the spring compression increases, and the rebound force increases linearly.

[0070] like Figure 1 , Figure 2As shown, in one embodiment, the torque input component further includes a servo motor 101 for driving the drive shaft 1 to rotate, a mounting plate 102, and a mounting base 103. The mounting plate 102 supports the servo motor 101 and is slidably connected to the mounting base 103. The mounting base 103 has a fixing member 104 for fixing the mounting plate 102. Specifically, the servo motor 101 provides a controlled rotational torque, and its output shaft is rigidly connected to the drive shaft 1 via a coupling, spline sleeve, or direct connection to drive the drive shaft 1 to rotate around the rotation axis X. The servo motor 101 has advantages such as fast response, high torque control accuracy, and programmable speed and angle settings. By connecting to a controller, the magnitude and duration of the rotational torque output by the servo motor 101 can be precisely controlled. When it is necessary to open or close the pressure relief valve, the controller sends a command to the servo motor 101 to output a rotational torque less than the maximum static friction torque. The drive shaft 1 drives the sleeve 2 and the transmission shaft 4 to rotate, completing the opening and closing action of the valve. When an overload occurs, the rotational torque output by the servo motor 101 exceeds the preset maximum static friction torque, causing relative sliding between the drive shaft 1 and the sleeve 2, interrupting torque transmission. At the same time, the current or torque feedback signal of the servo motor 101 will change instantaneously, allowing the controller to determine the overload state and stop the motor in time to avoid continuous idle rotation and heat generation.

[0071] To support the servo motor 101 and allow it to drive the torque output component for position adjustment, a mounting plate 102 and a mounting base 103 are provided. The mounting base 103 is a rigid base with guide rails, grooves, or guide planes on its surface (or mounting surface) along a direction perpendicular to the rotation axis X (or along the direction requiring adjustment). The servo motor 101 is fixedly mounted on the mounting plate 102 by screws or flanges. The surface of the mounting plate 102 matches the guide surface of the mounting base 103, for example, by providing sliders, bosses, or planes, allowing the mounting plate 102 to slide smoothly relative to the mounting base 103 in a predetermined direction.

[0072] In a preferred embodiment, the upper surface of the mounting base 103 has one or more T-shaped grooves parallel to the adjustment direction, and the lower surface of the mounting plate 102 is fixed with a T-shaped slider that mates with the T-shaped groove. After the slider is embedded in the groove, the mounting plate 102 can slide freely along the groove direction, but is constrained in a direction perpendicular to the sliding direction and vertically upward. By sliding the mounting plate 102, the position of components such as the drive shaft 1 can be changed to flexibly adapt to the installation needs of various scenarios.

[0073] In another embodiment, the mounting base 103 is provided with two parallel linear guide rails, and the bottom of the mounting plate 102 is fixed with a ball bearing slider that cooperates with the linear guide rails. The combination of these two components results in low sliding resistance and high precision, making it suitable for scenarios requiring frequent adjustments or high-precision alignment.

[0074] As another embodiment, to reduce costs or in applications with low adjustment frequency, a simple sliding structure using oblong holes and bolts can be adopted: the mounting base 103 has several oblong holes, and the mounting plate 102 has corresponding threaded holes. Bolts pass through the oblong holes and are screwed into the threaded holes of the mounting plate 102. After loosening the bolts, the mounting plate 102 can slide along the direction of the oblong holes, and is fixed after tightening the bolts. Therefore, the fixing member 104 can be adapted to different sliding mechanisms; to reduce costs, the fixing member 104 in this embodiment is a locking screw.

[0075] like Figure 4 , Figure 5 As shown, in another aspect, this embodiment also provides a transmission assembly, including a reducer 6, a propeller, and the aforementioned torque limiter. The reducer 6 includes a meshing first gear 601 and a second gear 602. The propeller is used to push or pull the torque limiter and to drive or disconnect the transmission shaft 4 from the first gear 601. Specifically, both the first gear 601 and the second gear 602 are bevel gears, and after meshing, they form a 90° steering transmission. The transmission shaft 4 of the torque limiter is used to drive the first gear 601, enabling the first gear 601 to drive the second gear 602 to rotate. Furthermore, the first gear 601 is provided with a square hole to accommodate the first connecting section 401 of the transmission shaft 4. Simultaneously, to facilitate the first connecting section 401 of the transmission shaft 4 extending into or out of the square hole, the torque limiter is pushed or pulled by the propeller (not shown), thereby changing the distance between the transmission shaft 4 and the first gear 601 to achieve drive or disconnection between them. Of course, the specific structure of the torque limiter described above refers to the above embodiments. Since this transmission component adopts all the technical solutions of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be elaborated here.

[0076] like Figure 4 , Figure 5 As shown, in another aspect, this embodiment also provides a piping system including a pressure relief valve 7 and the aforementioned transmission assembly. The pressure relief valve 7 is pulsatorically connected to the second gear 602 for opening and closing the pressure relief valve 7. Specifically, the valve stem of the pressure relief valve 7 is pulsatorically connected to the second gear 602, and the pressure relief valve 7 is opened and closed by the rotation of the second gear 602. Of course, the specific structure of the aforementioned transmission assembly is the same as described in the above embodiment. Since this piping system adopts all the technical solutions of the above embodiments, it at least has all the beneficial effects brought about by the technical solutions of the above embodiments, and will not be described in detail here.

[0077] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. A torque limiter characterized by, include: A torque input assembly includes a drive shaft configured to rotate in a controlled manner about a rotation axis; A torque output assembly includes a sleeve, an elastic element, and a drive shaft arranged along the rotation axis, the elastic element having a first end and a second end; The first end is configured to have a maximum static friction torque due to frictional transmission between the sleeve and the drive shaft. When the rotational torque of the drive shaft is greater than the maximum static friction torque, the drive shaft rotates relative to the sleeve and interrupts the torque transmission. The second end is configured to deform as the drive shaft moves along the rotation axis and accumulate a rebound force to drive the drive shaft to reset.

2. The torque limiter of claim 1, wherein, The drive shaft has a first connecting section extending along the axis of rotation, and the circumferential surface of the first connecting section is provided with at least one edge.

3. The torque limiter as described in claim 2, characterized in that, The drive shaft has a second connecting section, which is provided with an adjusting member configured to move in a controlled manner relative to the second connecting section to abut against the second end and to adjust the maximum static friction torque.

4. The torque limiter as described in claim 3, characterized in that, The first connecting segment and the second connecting segment are coaxial and detachably connected.

5. The torque limiter as described in claim 3, characterized in that, The adjusting component is a preload screw that is threadedly connected to the second connecting section.

6. The torque limiter as claimed in claim 1, characterized in that, The sleeve includes an inner tube and an outer tube that are slidably sleeved along the rotation axis. The inner tube is driven by friction with the drive shaft, and a receiving cavity is formed between the inner tube and the outer tube to accommodate the elastic element.

7. The torque limiter as described in any one of claims 1-6, characterized in that, The elastic element is a spring.

8. The torque limiter as described in any one of claims 1-6, characterized in that, The torque input assembly also includes a servo motor for driving the drive shaft to rotate, as well as a mounting plate and a mounting base. The mounting plate supports the servo motor and is slidably connected to the mounting base, which has fasteners for fixing the mounting plate.

9. A transmission assembly, characterized in that, The device includes a speed reducer, a propeller, and a torque limiter as described in any one of claims 1-8, wherein the speed reducer includes a meshing first gear and a second gear, and the propeller is used to push or pull the torque limiter and to drive or disconnect the drive shaft from the first gear.

10. A piping system, characterized in that, It includes a pressure relief valve and a transmission assembly as described in claim 9, wherein the pressure relief valve is connected to the second gear for opening and closing the pressure relief valve.

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