CN116972128B - Anti-locking ball screw - Google Patents
Anti-locking ball screw Download PDFInfo
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- CN116972128B CN116972128B CN202311228046.4A CN202311228046A CN116972128B CN 116972128 B CN116972128 B CN 116972128B CN 202311228046 A CN202311228046 A CN 202311228046A CN 116972128 B CN116972128 B CN 116972128B
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- screw
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- sleeve
- elastic
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- 230000005540 biological transmission Effects 0.000 claims abstract description 19
- 238000013459 approach Methods 0.000 claims abstract description 9
- 239000002783 friction material Substances 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 8
- 230000007704 transition Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 description 11
- 230000033001 locomotion Effects 0.000 description 9
- 230000003139 buffering effect Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 239000002131 composite material Substances 0.000 description 2
- 238000004663 powder metallurgy Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
- F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The application relates to the technical field of transmission devices, in particular to an anti-locking ball screw. The ball screw comprises a screw rod, a transmission ball, a screw nut and a buffer component. The transmission ball is abutted with the driving thread of the screw. The nut is sleeved on the outer periphery side of the screw rod. The transmission ball is arranged between the screw nut and the screw rod, and the screw rod rotating force drives the screw nut to move through the transmission ball. The slope subassembly of screw sets up the one end in the axial direction of screw. The thickness of the first end of the ramp assembly to the thickness of the second end of the ramp assembly increases gradually along a first direction of the circumference of the nut. The backup pad and the lead screw of buffer assembly can be dismantled and be connected. One end of the elastic unit of the buffer component is fixedly connected with the supporting plate, and the other end extends towards the direction of the slope component. When the screw rod rotates along the first direction of the circumference of the screw nut, the screw nut approaches the buffer component until the slope component is abutted with the elastic unit. Therefore, the problem of how to avoid damage to parts after the ball screw driving motor fails is solved.
Description
Technical Field
The application relates to the technical field of transmission devices, in particular to an anti-locking ball screw.
Background
The ball screw is one of key transmission elements for mutually converting rotary motion and linear motion in vehicle parts, and has great influence on the precision, efficiency and the like of equipment. When the motor driving the screw rod encounters an emergency such as abnormal power failure, failure occurs. At the moment, the screw rod is influenced by inertia to continuously drive the screw nut, the screw nut is influenced by inertia to continuously slide, and the screw nut is locked after moving out of a normal working stroke range and cannot be normally used. At present, the solution for avoiding such phenomenon can comprise the arrangement of a stop baffle ring at the end of the screw rod, and the limit of the screw nut is realized through the abutting connection of the stop baffle ring and the end of the screw nut.
After the motor for driving the screw rod fails suddenly, the screw rod can move to the stop baffle ring arranged at the end part of the screw rod at a very high speed under the drive of the screw rod and the inertia of the screw rod, so that the screw rod and the stop baffle ring are impacted, the screw rod is damaged or the screw rod is caused to slide out of the working thread area of the screw rod to cause the screw rod to be blocked, the screw rod cannot work again under the drive of the motor, and the parts are damaged.
Disclosure of Invention
In order to solve the problem of how to avoid damage to parts after failure of a ball screw driving motor, the application provides an anti-locking ball screw, which comprises the following components:
the outer periphery of the screw is provided with a driving thread;
a drive ball, the drive ball abutting the drive screw;
the nut comprises a body and a slope component; the body is sleeved on the outer periphery side of the screw rod; the transmission ball is arranged between the body and the screw, and the screw rotating force drives the nut to move through the transmission ball; the slope component is arranged at one end of the axial direction of the body; the ramp assembly includes a first end and a second end; the thickness from the first end of the slope component to the second end of the slope component gradually increases along the first direction of the circumference of the body;
the buffer assembly comprises a support plate and an elastic unit; the supporting plate is detachably connected with one end of the screw rod; one end of the elastic unit is fixedly connected with the supporting plate, and the other end extends towards the direction of the slope assembly; when the screw rod rotates along the first direction of the circumference of the body, the screw nut approaches to the buffer assembly until the slope assembly abuts against one end of the elastic unit.
In some embodiments, the support plate rotates in synchronization with the lead screw.
In some embodiments, the elastic unit comprises a first sleeve, an elastic part, a second sleeve and a brake part; one end of the first sleeve is fixedly connected with the supporting plate, and the other end extends towards the direction of the slope assembly; the second sleeve is sleeved on the outer periphery side or the inner periphery side of the first sleeve, and the second sleeve is axially and slidably connected with the first sleeve along the first sleeve; the elastic part is arranged in hollow areas inside the first sleeve and the second sleeve; two ends of the elastic part are respectively abutted against the inner end surfaces of the first sleeve and the second sleeve; the brake part is arranged at one end of the second sleeve, which is far away from the first sleeve; when the screw rod rotates along the first direction of the circumference of the body, the screw nut approaches to the buffer assembly until the slope assembly is abutted with the brake part.
In some embodiments, the braking portion is disposed obliquely along a first direction of the circumference of the body, and an oblique end surface of the braking portion is adapted to the ramp assembly.
In some embodiments, the brake is made using a friction material.
In some embodiments, the ramp assembly includes a first ramp unit, a second ramp unit; the first ramp unit includes a first end and a second end; the thickness from the first end of the first slope unit to the second end of the first slope unit gradually increases along the first direction of the circumference of the body; the second ramp unit includes a first end and a second end; the thickness from the first end of the second slope unit to the second end of the second slope unit gradually increases along the first direction of the circumference of the body; the second end of the first slope unit is in smooth transition connection with the first end of the second slope unit; the number of the elastic units is the same as the sum of the first ramp unit and the second ramp unit.
In some embodiments, the ramp assembly includes the same number of the first ramp unit and the second ramp unit; the first slope unit and the second slope unit are sequentially connected along the circumferential interval; the arc length of the first slope unit is longer than that of the second slope unit; the elastic units are uniformly arranged along the circumferential direction.
In some embodiments, 0.01.ltoreq.H1/L.ltoreq.0.1, 0.01.ltoreq.H2/L.ltoreq.0.1, wherein the difference in thickness between the first end and the second end of the first ramp unit is H1, the difference in thickness between the first end and the second end of the second ramp unit is H2, and the elastic unit has an amount of L along its axial direction.
In some embodiments, the roughness of the end surface of the ramp component, which abuts the elastic unit, is greater than or equal to 12.6.
In some embodiments, the external dimension of the driving thread of the nut moving distance section is larger than the external dimension of the driving thread of the nut working section in the process that the slope component and the elastic unit start to be abutted to the elastic unit to be compressed to the minimum length.
In order to solve the problem of how to avoid damage to parts after failure of the ball screw driving motor, the application has the following advantages:
the anti-lock ball screw may include: screw, transmission ball, screw, buffer assembly. The thickness of the first end of the slope subassembly of screw to the thickness of the second end of slope subassembly are followed the first direction of body circumference increases gradually, and when the screw is close to towards the buffer assembly until the slope subassembly and the one end butt of the elastic element of buffer assembly, at the elastic element of buffer assembly from the first end of slope subassembly to the slip in-process of second end, the buffer force of elastic element progressively increases, has reduced the impact force of screw to other spare part, plays the cushioning effect. Meanwhile, the movement of the screw nut can be slowed down, friction force is applied to the screw nut along the circumferential direction, and the rotation of the screw rod is slowed down. After the driving motor of the ball screw fails, the screw is influenced by inertia to continue to drive the screw, the screw approaches the buffer assembly until the slope assembly is abutted with one end of the elastic unit, at the moment, the elastic unit in the buffer assembly can reduce the impact force of the screw on other parts, the phenomenon that the screw moves out of the working range of the screw to damage the parts is avoided, and the ball screw can normally run after the failure of the driving motor is recovered is ensured.
Drawings
FIG. 1 illustrates a schematic view of an anti-lock ball screw of an embodiment;
FIG. 2 illustrates a schematic view of an anti-lock ball screw of another embodiment;
FIG. 3 illustrates a schematic view of a buffer assembly of an anti-lock ball screw according to one embodiment;
FIG. 4 illustrates a schematic view of a buffer assembly of an anti-lock ball screw of another embodiment;
fig. 5 shows a schematic view of the nut of an anti-lock ball screw according to one embodiment.
Reference numerals: 01 nut; 11 body; 12 ramp assembly; 121 a first ramp unit; 122 a second ramp unit; 02 a buffer assembly; a 21 support plate; 22 elastic units; 221 a first sleeve; 222 elastic parts; 223 second sleeve; 224 brake part; 03 lead screw; 31 rod body.
Detailed Description
The contents 5 of the present disclosure will now be discussed with reference to several exemplary embodiments. It should be understood that these embodiments are discussed only to enable those of ordinary skill in the art to better understand and thus practice the present disclosure, and are not meant to imply any limitation on the scope of the present disclosure.
As used herein, the term "comprising" and variants thereof are to be interpreted as meaning "including but not limited to" open-ended terms. The term "based on" is to be interpreted as "based at least in part on". The terms "one embodiment" and "an embodiment" are to be interpreted as "at least one embodiment. The term "another embodiment" is to be interpreted as "at least one other embodiment". The terms "upper", "lower", "left", "right", "front", "rear", "top", "bottom", "inner", "outer", "vertical", "horizontal", "transverse", "longitudinal", etc. refer to an orientation or positional relationship based on that shown in the drawings. These terms are only used to better describe the present application and its embodiments and are not intended to limit the scope of the indicated devices, elements or components to the particular orientations or to configure and operate in the particular orientations. Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in the present application will be understood by those of ordinary skill in the art according to the specific circumstances. Furthermore, the terms "mounted," "configured," "provided," "connected," and "connected" are to be construed broadly. For example, it may be a fixed connection, a removable connection, or a unitary construction; may be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements, or components. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances. Furthermore, the terms "first," "second," and the like, are used primarily to distinguish between different devices, elements, or components (the particular species and configurations may be the same or different), and are not used to indicate or imply the relative importance and number of devices, elements, or components indicated. Unless otherwise indicated, the meaning of "a plurality" is two or more.
The embodiment discloses an anti-lock ball screw, as shown in fig. 1 and 2, may include:
a screw 03, wherein a driving thread is arranged on the outer periphery of the screw 03;
the transmission ball is abutted with the driving thread;
the nut 01, the nut 01 includes the body 11, slope assembly 12; the body 11 is sleeved on the outer periphery side of the screw 03; the transmission ball is arranged between the body 11 and the screw 03, and the rotating force of the screw 03 drives the screw 01 to move through the transmission ball; the ramp assembly 12 is provided at one end of the body 11 in the axial direction; the ramp assembly 12 includes a first end and a second end; the thickness of the first end of the ramp component 12 to the thickness of the second end of the ramp component 12 increases gradually along the first direction of the circumference of the body 11;
a damper assembly 02, the damper assembly 02 including a support plate 21, an elastic unit 22; the supporting plate 21 is detachably connected with one end of the screw 03; one end of the elastic unit 22 is fixedly connected with the supporting plate 21, and the other end extends towards the direction of the slope assembly 12; when the screw 03 rotates in the first direction along the circumference of the body 11, the nut 01 approaches the buffer member 02 until the ramp member 12 abuts against one end of the elastic unit 22.
In this embodiment, the ball screw is one of indispensable components in the vehicle, the screw 03 can be driven by a motor to rotate around the screw 03 in the axial direction, and torque is transmitted to the nut 01 through the transmission ball, so that the axial linear movement of the nut 01 is realized. The ball screw can be arranged in the seat adjustment, so that passengers can adjust the position, the inclination angle and the height of the seat to obtain comfortable riding experience, and the ball screw can be arranged in a steering system for converting steering input of a driver into steering movement of front wheels to realize steering running of an automobile. When the driving motor of the ball screw fails, the nut 01 moving at high speed possibly moves out of the working range of the screw 03 to damage parts, so that key parts such as a steering wheel cannot work normally in the driving process, a vehicle cannot drive according to the intention of a driver, and driving safety is seriously endangered. In order to ensure that the ball screw can normally operate after the failure of the motor for driving the screw 03 is recovered, the ball screw can be improved into an anti-locking ball screw. As shown in fig. 1 and 2, the anti-lock ball screw may include: screw 03, drive ball, nut 01, buffer module 02. The screw 03 may include a drive thread, a rod body 31. The rod 31 may have a driving screw on its circumferential surface. The screw 03 may be used as a driving element in a ball screw. The nut 01 may include a body 11, a ramp assembly 12. The center of the body 11 is provided with a mounting hole along the axial direction, and the screw 03 can penetrate through the mounting hole. The circumference of the mounting hole can be provided with a thread corresponding to the driving thread of the screw rod 03, the driving thread of the screw rod 03 and the thread of the screw nut 01 can form a spiral space with a circular cross section, and the transmission ball can be embedded in the spiral space. When the ball screw is in an operating state, the rotational force of the screw 03 can drive the screw 01 to do linear motion by driving the ball. The transmission ball rolls, and the transmission ball is in rolling friction with the screw nut 01 and the screw rod 03 in a spiral space, so that the friction resistance can be effectively reduced, the running smoothness can be improved, the abrasion loss can be reduced, and the effect of improving the durability can be achieved. The ramp assembly 12 may be provided at one end of the body 11, and the ramp assembly 12 may include a first end and a second end, and the thickness of the first end may be smaller than the thickness of the second end. The thickness of the first end of the ramp component 12 to the thickness of the second end of the ramp component 12 may gradually increase in a ramp shape along a first direction of the circumference of the body 11. When the motor for driving the ball screw fails, inertia continuously rotates the screw 03, the screw 01 is driven to perform high-speed linear motion, then the slope assembly 12 is abutted with one end of the elastic unit 22, in the sliding process of the elastic unit 22 of the buffer assembly 02 from the first end to the second end of the slope assembly 12, the buffer force of the elastic unit 22 is gradually increased, the impact force of the screw 01 on other parts is reduced, a buffer effect is achieved, the movement of the screw 01 is slowed down, the friction force in the circumferential direction of the screw 01 is given, and the rotation of the screw 03 is slowed down. The damper assembly 02 may include a support plate 21, an elastic unit 22. The backup pad 21 can be dismantled with the one end of lead screw 03 and be connected, can be the bolted connection, block connection, round pin hub connection for the mode of dismantling, can carry out quick replacement according to user's demand or wearing and tearing volume, reaches reduce cost, improves work efficiency's effect. When the screw rod 03 rotates along the first direction of the circumference of the screw rod 01, the screw rod 01 approaches to the buffer component 02 until the slope component 12 is abutted against one end of the elastic unit 22, and when the slope component 12 contacts the elastic unit 22, the elastic unit 22 starts to compress and deform, and the impact force of the screw rod 01 on other components can be reduced by utilizing the buffer force provided during compression, so that the effect of avoiding damage of the screw rod 03 and the screw rod 01 is achieved.
In some embodiments, as shown in fig. 1 and 2, the support plate 21 rotates in synchronization with the lead screw 03.
In this embodiment, as shown in fig. 1 and 2, a mounting hole may be provided at the radial center of the support plate 21, and the support plate 21 may be detachably connected to one end of the screw 03, and rotate synchronously with the screw 03. When the motor for driving the screw 03 fails, the screw 03 is influenced by inertia to continue driving the screw 01, and the inertia of the screw 01 drives the screw 01, so that the screw 01 moves linearly toward the side provided with the support plate 21. When the end face of the nut 01 contacts with the buffer component 02 of the supporting plate 21, the nut 01 and the supporting plate 21 have a rotating speed difference, so that circumferential friction force is generated, the rotating speed of the screw 03 can be slowed down, the moving speed of the nut 01 is reduced, the impact force of the nut 01 on other parts is reduced, and the effect of avoiding the damage of the nut 01 is realized.
In some embodiments, as shown in fig. 3 and fig. 3, the elastic unit 22 includes a first sleeve 221, an elastic portion 222, a second sleeve 223, and a braking portion 224; one end of the first sleeve 221 is fixedly connected with the support plate 21, and the other end extends towards the slope assembly 12; the second sleeve 223 is sleeved on the outer circumference side or the inner circumference side of the first sleeve 221, and the second sleeve 223 is connected with the first sleeve 221 in a sliding manner along the axial direction of the first sleeve 221; the elastic part 222 is provided in a hollow region inside the first sleeve 221 and the second sleeve 223; both ends of the elastic portion 222 are respectively abutted against inner end surfaces of the first sleeve 221 and the second sleeve 223; the brake 224 is disposed at an end of the second sleeve 223 remote from the first sleeve 221; when the screw 03 rotates in the first direction along the circumference of the body 11, the nut 01 approaches the buffer assembly 02 until the ramp assembly 12 abuts the brake 224.
In the present embodiment, as shown in fig. 3 and 4, the elastic unit 22 may include a first sleeve 221, an elastic portion 222, a second sleeve 223, and a braking portion 224. One end of the first sleeve 221 may be fixedly connected to the support plate 21, and the other end extends away from the support plate 21. A hollow region may be provided at the inner side of the first sleeve 221. One end of the second sleeve 223 may be fitted over the outer circumferential side of the first sleeve 221 or may be fitted into the inner circumferential side of the first sleeve 221, and a hollow region corresponding to the hollow region of the first sleeve 221 may be provided inside. The second sleeve 223 is axially slidably connected to the first sleeve 221, and the sliding connection ensures that the second sleeve 223 moves in a fixed direction. The elastic portion 222 may be provided in hollow regions of the first sleeve 221 and the second sleeve 223, and both ends of the elastic portion 222 are respectively abutted against inner end surfaces of the first sleeve 221 and the second sleeve 223. When the nut 01 impacts the elastic unit 22, the impact force from the nut 01 can be relieved by the buffer force generated by compression of the elastic part 222, so that the parts can be protected from damage, and the effects of prolonging the service life, reducing noise and vibration are achieved. The material of the elastic portion 222 may include a spring, a pneumatic cylinder, and an oil hydraulic cylinder. When the cost of the elastic portion 222 is tightly controlled, the impact force is small, and a spring may be selected. When the elastic portion 222 needs to constantly adjust damping and resilience, a pneumatic cylinder may be selected. When the elastic portion 222 receives a large impact force, an oil cylinder may be selected. The braking portion 224 is disposed at an end of the second sleeve 223 remote from the first sleeve 221, and a friction coefficient of the braking portion 224 may be relatively large. When the motor for driving the screw 03 fails, the screw 03 continues to rotate along the first direction along the circumference of the body 11 under the influence of inertia to drive the screw 01, and the inertia of the screw 01 also drives the screw 01, so that the screw 01 moves at a high speed toward the buffer assembly 02. When the end face of the screw 01 is abutted against the braking part 224, the large friction resistance between one end of the braking part 224 and the slope component 12 can brake the rotation of the screw 03, so that the rotation speed of the screw 03 is reduced, and the effect of reducing the impact force is achieved.
In some embodiments, as shown in fig. 3 and 4, the braking portion 224 is disposed obliquely along a first direction of the circumference of the body 11, and an inclined end surface of the braking portion 224 is adapted to the ramp assembly 12.
In this embodiment, since the first end and the second end of the ramp component 12 are gradually thickened along the first direction of the circumference of the nut 01, in order to make the contact area between the brake portion 224 and the ramp component 12 be larger after the contact, the friction force is more fully exerted, the brake portion 224 can be obliquely arranged along the first direction of the circumference of the nut 01, so that the oblique end face of the brake portion 224 is adapted to the ramp component 12, and the effect of reducing the rotation speed of the screw 03 while providing larger circumferential friction force is achieved.
In some embodiments, as shown in FIG. 4, the brake 224 is made using a friction material.
In this embodiment, as shown in fig. 4, the brake 224 may be made of a friction material, which may include a composite rubber material, a powder metallurgy friction material. When the working environment temperature is low, the rotation speed of the screw 03 and the moving speed of the screw 01 are low, a composite rubber material can be adopted, and the cost can be controlled while the working requirement is met. When the working environment temperature, the rotation speed of the screw 03 and the moving speed of the screw 01 are higher, powder metallurgy friction materials can be adopted, and even if the temperature is increased due to friction of parts, the braking effect can be ensured, so that the parts are not damaged. When the nut 01 is abutted against the braking part 224, the braking part 224 using the friction material can be composed of a plurality of particles on the surface of the friction material, so that the surface area contacted with air is larger, and the heat dissipation is facilitated. The friction material may be less stiff and elastically deformed upon abutment with the ramp assembly 12 may reduce noise generation. The high friction coefficient of the friction material can effectively reduce the rotating speed of the screw rod 03, and the impact force of the screw nut 01 on other parts is reduced.
In some embodiments, as shown in fig. 5, the ramp assembly 12 includes a first ramp unit 121, a second ramp unit 122; the first ramp unit 121 includes a first end and a second end; the thickness of the first end of the first slope unit 121 to the thickness of the second end of the first slope unit 121 gradually increases along the first direction of the circumference of the body 11; the second ramp unit 122 includes a first end and a second end; the thickness of the first end of the second ramp unit 122 to the thickness of the second end of the second ramp unit 122 gradually increases along the first direction of the circumference of the body 11; the second end of the first slope unit 121 is in smooth transition connection with the first end of the second slope unit 122; the number of elastic units 22 is the same as the sum of the number of first and second slope units 121 and 122.
In this embodiment, as shown in fig. 5, the ramp component 12 is disposed at one end of the body 11, and may include a first ramp unit 121 and a second ramp unit 122. Simultaneously, a plurality of slopes are arranged, so that the contact area between the slope assembly 12 and the brake 224 is larger, the stress is more uniform when the impact force is born, and the situation that the motor fails when the screw 03 is driven can be ensured, and after the screw 01 is contacted with the buffer assembly 02, the screw 01 is not damaged. The first and second ramp units 121 and 122 may include first and second ends. The thicknesses of the first ends of the first and second ramp units 121 and 122 to the thicknesses of the second ends of the first and second ramp units 121 and 122 may gradually increase in the first direction along the circumference of the body 11. When the nut 01 moves to the slope assembly 12 to be abutted against the braking portion 224 of the elastic unit 22, in the sliding process of the braking portion 224 from the first end to the second end of the first slope unit 121 and the second slope unit 122, the buffer force of the elastic unit 22 is gradually increased, the impact force of the nut 01 on other parts is reduced, the buffering effect is achieved, the movement of the nut 01 is slowed down, and a friction moment of the nut 01 in the opposite direction along the first direction is given, so that the rotation of the screw 03 is slowed down. The second end of the first slope unit 121 and the first end of the second slope unit 122 may be in smooth transition connection, in this way, the brake 224 may be moved from the second end of the first slope unit 121 to the first end of the second slope unit 122 in a sliding manner, no additional impact force is generated, and it may be ensured that the nut 01 is not damaged after the motor for driving the screw 03 fails. The number of the elastic units 22 may be the same as that of the first slope units 121 and the second slope units 122, when the slope assembly 12 is abutted against the braking portion 224, each first slope unit 121 or each second slope unit 122 may be in contact with the braking portion 224, so that each first slope unit 121 or each second slope unit 122 is fully utilized, the maximum circumferential friction force is exerted, and the rotation speed of the screw 03 can be reduced at the fastest speed.
In some embodiments, as shown in fig. 5, the ramp assembly 12 includes the same number of first and second ramp units 121 and 122; the first ramp unit 121 and the second ramp unit 122 are sequentially connected at intervals in the circumferential direction; the arc length of the first slope unit 121 is longer than that of the second slope unit 122; the plurality of elastic units 22 are uniformly disposed in the circumferential direction.
In this embodiment, as shown in fig. 5, the ramp assembly 12 may include the same number of first ramp units 121 and second ramp units 122, and the first ramp units 121 may be sequentially connected with the second ramp units 122 at intervals in the circumferential direction. Since the elastic units 22 are uniformly disposed in the circumferential direction and the number of the elastic units 22 is the same as the sum of the numbers of the first and second slope units 121 and 122, the first and second slope units 121 and 122 may be uniformly connected in the circumferential direction. When the brake portions 224 are abutted against the ramp assembly 12, it is ensured that the two brake portions 224 opposed in the radial direction simultaneously generate friction force in the circumferential direction at the same rate, the rotation speed of the screw 03 is reduced, and the increase of impact force of the screw 01 on other parts due to excessive vibration generated by the screw 01 can be avoided. The arc length of the first slope unit 121 may be greater than that of the second slope unit 122, when the braking portion 224 abuts against the slope assembly 12, and the braking portion 224 moves from the second end of the first slope unit 121 to the first end of the second slope unit 122 or the second end of the second slope unit 122 to the first end of the first slope unit 121, the braking portion 224 may be dropped at two different time points, so that all the braking portions 224 are prevented from being dropped at the same time, and a substantial failure of buffering force may be alleviated. The plurality of elastic units 22 can be uniformly arranged along the circumferential direction, so that when the brake part 224 is contacted with the slope component 12, the brake part 224 is prevented from being irregularly lifted by the slope component 12 and then falls back down, so that redundant vibration is generated, redundant impact force is generated, and the effect of reducing the impact force of the slope component 12 on the brake part 224 is achieved.
In some embodiments, as shown in FIG. 5, 0.01.ltoreq.H2/L.ltoreq.0.1, wherein the difference in thickness between the first end and the second end of the first slope unit 121 is H1, the difference in thickness between the first end and the second end of the second slope unit 122 is H2, and the elastic unit 22 is deformed by L in the axial direction thereof.
In this embodiment, as shown in fig. 5, H1 may be a thickness difference between the first end and the second end of the first ramp unit 121, H2 may be a thickness difference between the first end and the second end of the second ramp unit 122, and L may be an axial deformation amount of the elastic unit 22. The ratio of H1 to L may be greater than or equal to 0.01 and less than or equal to 0.1, when the elastic unit 22 abuts against the ramp component 12, the thickness difference between the first end and the second end of the first ramp unit 121 may make the thickness difference between the first end and the second end of the first ramp unit 121 affect the compression stroke of the current elastic portion 222 less, which is insufficient to affect the buffering force generated when the elastic portion 222 is compressed, so as to ensure that the impact force is absorbed by the elastic portion 222, and the nut 01 is not damaged. The ratio of H2 to L may be greater than or equal to 0.01 and less than or equal to 0.1, when the elastic unit 22 abuts against the ramp component 12, the thickness difference from the first end of the second ramp unit 122 to the second end of the second ramp unit 122 may have a smaller influence on the compression stroke of the current elastic portion 222, and is insufficient to influence the buffering force generated when the elastic portion 222 is compressed, so that the impact force can be absorbed by the elastic portion 222, and the nut 01 is not damaged.
In some embodiments, as shown in fig. 5, the roughness of the end surface of the ramp assembly 12 abutting the elastic unit 22 is 12.6 or more.
In the present embodiment, as shown in fig. 5, the roughness of the end surface of the ramp component 12 abutting against the elastic unit 22 may be 12.6 or more. When the ramp component 12 abuts against the braking portion 224 of the elastic unit 22, the end surface of the ramp component 12 abutting against the elastic unit 22 rubs, and if the roughness is too small, the applied circumferential friction force is insufficient, the rotation speed of the screw 03 and the moving speed of the nut 01 cannot be quickly reduced, and the ramp component 12 and the elastic unit 22 are damaged. When the roughness of the end surface of the slope component 12, which is abutted against the elastic unit 22, can be more than or equal to 12.6, enough circumferential friction force can be applied, so that the rotation speed of the screw 03 and the moving speed of the nut 01 can be quickly reduced, and the slope component 12 and the elastic unit 22 can be protected to be used continuously.
In some embodiments, as shown in fig. 1 and 2, the external dimension of the driving thread of the moving distance section of the nut 01 is larger than the external dimension of the driving thread of the working section of the nut 01 in the process that the slope assembly 12 and the elastic unit 22 start to be abutted to the elastic unit 22 to be compressed to the minimum length.
In this embodiment, as shown in fig. 1 and 2, the external dimension of the driving thread of the moving distance section of the nut 01 may be processed to be larger than the external dimension of the driving thread of the working section of the nut 01 in the process that the slope assembly 12 and the elastic unit 22 start to be abutted against the elastic unit 22 and compress until the nut 01 stops moving. When the nut 01 moves on the large-size driving thread, the large-size driving thread can apply an extra resistance to the nut 01 (the resistance causes little damage to parts), so that the moving speed of the nut 01 can be slowed down, the impact force of the nut 01 on other parts is reduced, and the nut 01 is prevented from being damaged.
It will be understood by those of ordinary skill in the art that the foregoing embodiments are specific examples of implementing the disclosure, and that various changes in form and details may be made therein without departing from the spirit and scope of the disclosure.
Claims (9)
1. An anti-lock ball screw, comprising:
the outer periphery of the screw is provided with a driving thread;
a drive ball, the drive ball abutting the drive screw;
the nut comprises a body and a slope component; the body is sleeved on the outer periphery side of the screw rod; the transmission ball is arranged between the body and the screw, and the screw rotating force drives the nut to move through the transmission ball; the slope component is arranged at one end of the axial direction of the body; the ramp assembly includes a first end and a second end; the thickness from the first end of the slope component to the second end of the slope component gradually increases along the first direction of the circumference of the body;
the buffer assembly comprises a support plate and an elastic unit; the supporting plate is detachably connected with one end of the screw rod; one end of the elastic unit is fixedly connected with the supporting plate, and the other end extends towards the direction of the slope assembly; when the screw rod rotates along the first direction of the circumference of the body, the screw nut approaches to the buffer assembly until the slope assembly is abutted against one end of the elastic unit;
the slope component comprises a first slope unit and a second slope unit; the first ramp unit includes a first end and a second end; the thickness from the first end of the first slope unit to the second end of the first slope unit gradually increases along the first direction of the circumference of the body; the second ramp unit includes a first end and a second end; the thickness from the first end of the second slope unit to the second end of the second slope unit gradually increases along the first direction of the circumference of the body; the second end of the first slope unit is in smooth transition connection with the first end of the second slope unit; the number of the elastic units is the same as the sum of the first ramp unit and the second ramp unit.
2. An anti-lock ball screw as claimed in claim 1, wherein,
the support plate and the screw rod rotate synchronously.
3. An anti-lock ball screw as claimed in claim 1 or 2, wherein,
the elastic unit comprises a first sleeve, an elastic part, a second sleeve and a brake part; one end of the first sleeve is fixedly connected with the supporting plate, and the other end extends towards the direction of the slope assembly; the second sleeve is sleeved on the outer periphery side or the inner periphery side of the first sleeve, and the second sleeve is axially and slidably connected with the first sleeve along the first sleeve; the elastic part is arranged in hollow areas inside the first sleeve and the second sleeve; two ends of the elastic part are respectively abutted against the inner end surfaces of the first sleeve and the second sleeve; the brake part is arranged at one end of the second sleeve, which is far away from the first sleeve; when the screw rod rotates along the first direction of the circumference of the body, the screw nut approaches to the buffer assembly until the slope assembly is abutted with the brake part.
4. An anti-lock ball screw as claimed in claim 3, wherein,
the brake part is arranged along the first direction of the circumference of the body in an inclined mode, and the inclined end face of the brake part is matched with the slope assembly.
5. An anti-lock ball screw as claimed in claim 3, wherein,
the brake part is made of friction materials.
6. An anti-lock ball screw as claimed in claim 1, wherein,
the ramp assembly includes the same number of the first ramp unit and the second ramp unit; the first slope unit and the second slope unit are sequentially connected along the circumferential interval; the arc length of the first slope unit is longer than that of the second slope unit; the elastic units are uniformly arranged along the circumferential direction.
7. An anti-lock ball screw as claimed in claim 6, wherein,
H1/L is more than or equal to 0.01 and less than or equal to 0.1, H2/L is more than or equal to 0.01 and less than or equal to 0.1, wherein the thickness difference between the first end and the second end of the first slope unit is H1, the thickness difference between the first end and the second end of the second slope unit is H2, and the deformation amount of the elastic unit along the axial direction of the elastic unit is L.
8. An anti-lock ball screw as claimed in claim 1, wherein,
the roughness of the end surface of the slope component, which is abutted against the elastic unit, is more than or equal to 12.6.
9. An anti-lock ball screw as claimed in claim 1, wherein,
and in the process that the slope component and the elastic unit are abutted to the elastic unit to be compressed to the minimum length, the external dimension of the driving screw thread of the screw moving distance section is larger than that of the driving screw thread of the screw working section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311228046.4A CN116972128B (en) | 2023-09-22 | 2023-09-22 | Anti-locking ball screw |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311228046.4A CN116972128B (en) | 2023-09-22 | 2023-09-22 | Anti-locking ball screw |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN116972128A CN116972128A (en) | 2023-10-31 |
| CN116972128B true CN116972128B (en) | 2023-12-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311228046.4A Active CN116972128B (en) | 2023-09-22 | 2023-09-22 | Anti-locking ball screw |
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| Country | Link |
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| CN (1) | CN116972128B (en) |
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| US2504018A (en) * | 1945-11-15 | 1950-04-11 | Curtiss Wright Corp | Screw operated clutch |
| US4266437A (en) * | 1979-01-31 | 1981-05-12 | Warner Electric Brake & Clutch Company | Ball screw and nut assembly |
| JPH09324845A (en) * | 1996-06-03 | 1997-12-16 | Thk Kk | Stopper device for ball screw |
| JP2011052834A (en) * | 2010-12-14 | 2011-03-17 | Nsk Ltd | Ball screw |
| CN102414478A (en) * | 2009-04-23 | 2012-04-11 | 埃尔塞乐公司 | Torque limiter in particular for actuator of nacelle of aircraft turbojet engine |
| DE102014008329A1 (en) * | 2014-06-12 | 2015-12-17 | Siemens Aktiengesellschaft | Gear for converting a rotational movement into a linear movement |
| CN108884889A (en) * | 2016-03-10 | 2018-11-23 | 卢卡斯汽车有限公司 | Axis nut assembly with multiple brake cams |
| CN218543087U (en) * | 2022-08-01 | 2023-02-28 | 南通泰尔精密机械有限公司 | Self-pretightening ball screw pair |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20010029797A1 (en) * | 2000-04-27 | 2001-10-18 | Thomson Saginaw Ball Screw Company, L.L.C. | Multiple stage, multiple extend, speed reducing ball screw linear actuator and method of constructing and operating the actuator |
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Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2504018A (en) * | 1945-11-15 | 1950-04-11 | Curtiss Wright Corp | Screw operated clutch |
| US4266437A (en) * | 1979-01-31 | 1981-05-12 | Warner Electric Brake & Clutch Company | Ball screw and nut assembly |
| JPH09324845A (en) * | 1996-06-03 | 1997-12-16 | Thk Kk | Stopper device for ball screw |
| CN102414478A (en) * | 2009-04-23 | 2012-04-11 | 埃尔塞乐公司 | Torque limiter in particular for actuator of nacelle of aircraft turbojet engine |
| JP2011052834A (en) * | 2010-12-14 | 2011-03-17 | Nsk Ltd | Ball screw |
| DE102014008329A1 (en) * | 2014-06-12 | 2015-12-17 | Siemens Aktiengesellschaft | Gear for converting a rotational movement into a linear movement |
| CN108884889A (en) * | 2016-03-10 | 2018-11-23 | 卢卡斯汽车有限公司 | Axis nut assembly with multiple brake cams |
| CN218543087U (en) * | 2022-08-01 | 2023-02-28 | 南通泰尔精密机械有限公司 | Self-pretightening ball screw pair |
Also Published As
| Publication number | Publication date |
|---|---|
| CN116972128A (en) | 2023-10-31 |
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