Braking force device and elevator

Abstract

This application relates to a braking device and an elevator. The braking device includes a mating member and a braking mechanism. The mating member extends along a first direction; the braking mechanism is disposed on at least one side of the mating member along the first direction, and includes a bracket, a lifting member, a friction element, and an elastic element. The lifting member, friction element, and elastic element are located within the bracket. One end of the friction element is connected to the lifting member, and the other end is movably connected to the elastic element. The friction element is disposed between the mating member and the elastic element along a second direction, which intersects the first direction. In the braking state, the friction element moves relative to the bracket along the first direction under the action of the lifting member, and can roll and abut against the mating member, and compress the elastic element along the second direction. The elastic element applies a force to the friction element in the first and second directions. When the braking device provided in the embodiment of this application is in the braking state, the friction element rolls relative to the mating member without damaging the mating member, and the braking force is determined by the friction element itself.

Description

Technical Field

[0001] This application relates to the field of elevator braking technology, and in particular to braking devices and elevators. Background Technology

[0002] The braking device is a crucial component of elevator equipment, playing a vital role in enhancing safety protection. It is typically installed on the lower sides of the elevator car. When the elevator malfunctions and falls at excessive speed, reaching the speed limiter's activation point, the speed limiter activates the braking device to bring the elevator car to a safe stop, clamping it onto the locking mechanism to prevent accidents and increase the elevator's safety factor.

[0003] Due to differences in processing methods, surface protection, operating conditions, manufacturing errors, and external factors such as rust and oil contamination, the friction factors can vary considerably. This means that traditional braking devices cannot meet the safety requirements of stopping the elevator under all operating conditions, severely impacting braking capacity. This is especially true in the elevator retrofitting market, where the condition of old elevators and their old components is diverse and cannot be matched one by one. Choosing a safety clamp hastily could easily lead to the risk of failing to stop the elevator.

[0004] However, the braking devices that currently use sliding friction braking often result in scratches on the mating parts during use. As the number of times the braking device is used increases, the damage to the mating parts intensifies, and the damaged mating parts lead to a serious decrease in braking performance, affecting elevator safety.

[0005] Therefore, there is an urgent need for a braking device that causes minimal damage to the mating components and whose braking force is unaffected by changes in the friction factors of the mating components. Summary of the Invention

[0006] Therefore, it is necessary to provide a braking device and an elevator to address the problems of severe wear of the mating parts during operation, which affects the service life of the mating parts, and the instability of braking force caused by different friction factors of the mating parts.

[0007] A braking force device, comprising:

[0008] The dual component extends along the first direction;

[0009] A braking mechanism is provided on at least one side of the mating member along the first direction. The braking mechanism includes a bracket, a lifting member, a friction element, and an elastic element. The lifting member, the friction element, and the elastic element are located within the bracket. One end of the friction element is connected to the lifting member, and the other end is movably connected to the elastic element. The friction element is provided between the mating member and the elastic element along a second direction, which intersects with the first direction.

[0010] When in a braking state, the friction element moves relative to the bracket in the first direction under the action of the lifting member, can roll and abut against the mating member, and compresses the elastic member in the second direction. The elastic member applies a force to the friction element in the first and second directions.

[0011] In one embodiment, the braking device further includes a stop member disposed above the friction element in the first direction, such that before the friction element and the stop member abut, the damping wheel of the friction element can abut against the mating member and remain stationary relative to the mating member.

[0012] In one embodiment, the friction element includes the damping wheel and the mounting base, the mounting base being connected to the lifting member and the elastic member, the damping wheel being rotatably connected to the mounting base and located between the mounting base and the mating member;

[0013] When in the braking state, the damping wheel and the mating member roll and abut against each other; when in the normal state, the damping wheel and the mating member are spaced apart.

[0014] In one embodiment, the friction element further includes a translation member, one end of which is movably connected to the mounting base and the other end of which is connected to the elastic member. In the second direction, the translation member is capable of moving along the bracket and pressing the elastic member.

[0015] In one embodiment, the translation member has an inclined surface toward the mating member, and the distance between the inclined surface and the mating member gradually increases from the end where the stop member is located along the first direction.

[0016] In one embodiment, the friction element further includes a rolling element disposed between the mounting base and the inclined surface.

[0017] In one embodiment, the tilt angle formed between the tilted surface of the translation member and the support is α, the lifting force on the friction element is T, the lifting force includes the lifting force applied by the lifting member to the friction element and the friction force generated between the friction element and the mating member, and the pressure applied by the elastic member to the mating member along the second direction is P1, where T > P1 × sinα × cosα.

[0018] In one embodiment, the rotational resistance of the damping wheel itself is f, the coefficient of friction between the damping wheel and the mating member is μ, and in the braking state, when the mounting base and the stop member abut, and the elastic member deforms, the pressure applied by the damping wheel to the mating member along the second direction is P2, where f < μ × P2.

[0019] In one embodiment, the braking mechanism is symmetrically arranged with respect to the mating member.

[0020] An elevator, the elevator including the braking force device described in any of the above embodiments.

[0021] In the aforementioned braking device and elevator, when the braking device is in braking mode, the friction element, under the combined action of the lifting component and the elastic component, approaches and acts on the mating component. Furthermore, throughout the entire operation, the friction element initially remains stationary relative to the mating component. Once the friction element and the stop component come into contact, the damping wheel rotates, generating rolling friction. Therefore, the wear on the mating component is minimal and does not affect its service life. Since the damping wheel rotates until the elevator stops, the resistance experienced by the elevator from the time the damping wheel rotates to the time it stops comes from the rotational resistance of the damping wheel itself, unaffected by the mating component, thus providing stable braking force. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the braking device provided in some embodiments of this application when it is in a normal state.

[0023] Figure 2 This is a schematic diagram of a braking device provided in some embodiments of this application, where the elastic element is not compressed while the device is in a braking state.

[0024] Figure 3 This is a schematic diagram of a braking device provided in some embodiments of this application, where the elastic element is compressed while the device is in a braking state.

[0025] Explanation of reference numerals in the attached figures:

[0026] 100. Braking device;

[0027] 10. Coupled component; 20. Braking mechanism; 21. Bracket; 22. Lifting component; 23. Friction element; 231. Damping wheel; 232. Mounting base; 233. Translation component; 2331. Inclined surface; 234. Rolling component; 24. Elastic component; 30. Stop component;

[0028] X, the first direction; Y, the second direction. Detailed Implementation

[0029] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0030] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0031] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0032] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0033] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0034] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0035] Please see Figures 1 to 3 This application provides a braking device 100 in some embodiments. The braking device 100 includes a mating member 10 and a braking mechanism 20. The mating member 10 extends along a first direction X; the braking mechanism 20 is disposed on at least one side of the mating member 10 along the first direction X. The braking mechanism 20 includes a bracket 21, a lifting member 22, a friction element 23, and an elastic element 24. The lifting member 22, the friction element 23, and the elastic element 24 are located within the bracket 21. One end of the friction element 23 is connected to the lifting member 22, and the other end is movably connected to the elastic element 24. The friction element 23 is disposed between the mating member 10 and the elastic element 24 along a second direction Y, which intersects the first direction X.

[0036] When in braking state, the friction element 23 moves relative to the bracket 21 in the first direction X under the action of the lifting member 22, and can roll and abut against the mating member 10, and compress the elastic member 24 in the second direction Y. The elastic member 24 applies a force to the friction element 23 in the first direction X and the second direction Y.

[0037] The working principle of the braking force device 100 will be explained below in the application scenario of the braking force device 100 being used in an elevator car.

[0038] Please see Figure 1 The mating member 10 extends along the first direction X, and the elevator car can move relative to the mating member 10 along the first direction X, where the first direction X can be understood as the vertical direction.

[0039] The braking device 100 is movably installed at the bottom of the elevator car. When the elevator's operating speed is within the normal range, the braking device 100 is in normal condition, and the friction element 23 and the mating part 10 are not in contact. When the elevator car descends at excessive speed, the braking device 100 switches from the normal state to the braking state, and the braking device 100 begins to operate.

[0040] The specific operation of the braking device 100 is as follows: the speed governor installed in the car applies an upward lifting force to the lifting member 22. Driven by the lifting member 22, the friction element 23 initially comes to rest relative to the mating member 10 in the first direction X. As the elevator car descends, it moves the support 21 downwards as well. Due to the upward pulling force of the lifting member 22, the friction element 23 gradually approaches and comes into contact with the mating member 10.

[0041] When the friction element 23 and the mating member 10 come into contact, the friction element 23, driven by the pulling force applied by the lifting member 22, remains stationary relative to the mating member 10 in the first direction X. As the support 21 continues to move downward relative to the friction element 23, the friction element 23 compresses the elastic member 24 along the second direction Y, causing the elastic member 24 to deform and generate an elastic restoring force. The elastic member 24 can apply a force along the first direction X and a force along the second direction Y to the friction element 23. The second direction Y is perpendicular to the first direction X. At this time, the force applied by the elastic member 24 to the friction element 23 along the second direction Y can be understood as the horizontal direction in the figure.

[0042] As the support 21 moves downward relative to the friction element 23, the compression of the elastic element 24 gradually intensifies, the elastic restoring force generated by the elastic element 24 gradually increases, and the force it exerts on the friction element 23 also gradually increases. If the sum of the lifting force exerted by the lifting element 22 on the friction element 23 and the friction force generated between the friction element 23 and the mating element 10 is greater than the downward thrust exerted by the elastic element 24 on the friction element 23, the friction element 23 will remain stationary relative to the mating element 10. When the friction element 23 and the support 21 come into contact, and the friction element 23 and the support 21 no longer move relative to each other along the first direction X, the braking force device 100 completes the braking deformation operation. Subsequently, the parts of the friction element 23 that can roll into contact with the mating element 10 begin to operate. For example, the damping wheel 231 of the friction element 23 begins to rotate and generates its own rotational resistance, thus officially providing braking force to stop the elevator. During this process, because the friction element 23 is in rolling contact with the mating part 10, the wear on the mating part 10 is relatively small, while the force that provides deceleration for the elevator car comes from the rotational resistance f generated by the damping wheel 231.

[0043] In summary, when the braking device 100 is in braking state, the friction element 23 can approach and act on the mating part 10 under the combined action of the lifting member 22 and the elastic member 24. Moreover, throughout the entire operation, the friction element 23 is in rolling contact with the mating part 10. Therefore, the wear on the mating part 10 is small and will not affect the service life of the mating part 10.

[0044] The mating component 10 in this embodiment can be understood as the guide rail structure in an elevator. Due to different processing methods, surface protection, operating conditions, manufacturing errors, or factors such as rust and oil contamination, the coefficient of friction on the mating component 10 can vary within a large range. Therefore, traditional braking devices 100 cannot meet the design requirements of the mating component 10 under different operating conditions and cannot guarantee a constant braking force. Therefore, the braking device 100 of this application is introduced, which can effectively meet the design requirements of different friction coefficients and guarantee a constant braking force.

[0045] In some embodiments, the braking device 100 further includes a stop 30, which is disposed above the friction element 23 in the first direction X. Before the friction element 23 and the stop 30 come into contact, the damping wheel 231 of the friction element 23 can come into contact with the mating member 10 and remain stationary relative to the mating member 10.

[0046] The structure of the stop 30 can be, but is not limited to, block-shaped. The stop 30 can be mounted on the bracket 21, and the number of stop 30s can correspond one-to-one with the number of mounting seats 232. That is, one mounting seat 232 is equipped with one stop 30. A channel can be reserved between the stop 30 and the mating part 10 for the lifting part 22 to run.

[0047] In the initial stage of braking, the mating member 10 and the friction element 23 are relatively stationary. When the lifting member 22 moves the friction element 23 upward relative to the support 21, the damping wheel 231 of the friction element 23 first abuts against the mating member 10. At this time, there is still a distance between the friction element 23 and the stop member 30. As the lifting member 22 moves, the friction element 23 continues to move upward relative to the support 21, and the force exerted on the friction element 23 by the elastic member 24 gradually increases until the friction element 23 abuts against the stop member 30, and the braking force device 100 completes the braking deformation operation.

[0048] After the friction element 23 and the stop 30 come into contact, the bracket 21 continues to move downwards. Then, the damping wheel 231 of the friction element 23 begins to rotate, generating its own rotational resistance. Thus, the braking force device 100 begins to provide braking force to the elevator car to stop it. During this process, because the friction element 23 is in rolling contact with the mating part 10, the wear on the mating part 10 is relatively small. The force providing deceleration for the elevator comes from the rotational resistance generated by the damping wheel 231 itself. It should be noted that because the damping wheel 231 can roll relative to the mating part 10, the magnitude of the deceleration resistance during the elevator car's descent mainly depends on the resistance of the damping wheel 231.

[0049] Thus, by setting the stop 30, the friction element 23 can be limited, and the distance that the damping wheel 231 of the friction element 23 moves relative to the mating part 10 after it comes into contact with the mating part 10 can be controlled, thereby reducing the amount of wear on the mating part 10.

[0050] In some embodiments, the friction element 23 includes a damping wheel 231 and a mounting base 232. The mounting base 232 is connected to a lifting member 22 and an elastic member 24. The damping wheel 231 and the mounting base 232 are rotatably connected and are located between the mounting base 232 and the mating member 10. When in a braking state, the damping wheel 231 and the mating member 10 roll against each other. When in a normal state, the damping wheel 231 and the mating member 10 are spaced apart.

[0051] The shape of the mounting base 232 can be, but is not limited to, trapezoidal. The mounting base 232 includes two sides arranged opposite each other along the second direction Y. A damping wheel 231 is connected to one side, and an elastic member 24 is connected to the other side. The mounting base 232 and the damping wheel 231 can be detachably connected, and the mounting base 232 and the elastic member 24 can also be detachably connected.

[0052] During the transition of the braking device 100 from normal to braking state, the damping wheel 231 and the mounting base 232 move closer to the mating member 10 under the action of the lifting member 22. This continues until the mounting base 232 and the stop member 30 come into contact. Throughout this process, the elastic member 24 remains compressed, applying force to the mounting base 232 and the damping wheel 231. This ensures that the damping wheel 231 has sufficient positive pressure P against the mating member 10 under this force, guaranteeing that the sum of the lifting force applied by the lifting member 22 to the friction element 23 and the frictional force generated between the friction element 23 and the mating member 10 is greater than the downward thrust exerted by the elastic member 24 on the friction element 23. This allows the damping wheel 231 and the mating member 10 to remain relatively stationary before the mounting base 232 and the stop member 30 come into contact.

[0053] By including a damping wheel 231 and a mounting base 232 in the friction element 23, the friction element 23 can be made to roll relative to the mating member 10 while simplifying its structure.

[0054] Furthermore, such as Figure 2 and Figure 3 As shown, in some embodiments, the friction element 23 further includes a translation member 233. One end of the translation member 233 is movably connected to the mounting base 232, and the other end is connected to an elastic member 24. In the second direction Y, the translation member 233 can move along the bracket 21 and compress the elastic member 24.

[0055] The translation member 233 and the mounting base 232 may be, but are not limited to, a rolling connection. For example, when the translation member 233 moves, it can drive the mounting base 232 to move together.

[0056] When the lifting member 22 drives the mounting base 232 to move upward relative to the bracket 21, the mounting base 232 can drive the translation member 233 to move along the bracket 21 in the direction of continuously compressing the elastic member 24, so that the elastic member 24 deforms and generates an elastic restoring force. Before the deformation of the elastic member 24 reaches its maximum value, the mounting base 232 and the stop member 30 must come into contact. At this time, the force exerted by the elastic member 24 on the mounting base 232 and the damping wheel 231 reaches its maximum.

[0057] The above configuration utilizes the mounting base 232, which moves relative to the support 21 in the first direction X, to drive the translation member 233 to move in the second direction Y, thereby compressing the elastic member 24. This achieves linkage between movements in two different directions and simplifies the method of driving the elastic member 24 to move in the second direction Y.

[0058] Specifically, in some embodiments, the translation member 233 has an inclined surface 2331 facing the mating member 10, and the distance between the inclined surface 2331 and the mating member 10 gradually increases from the end where the stop member 30 is located along a first direction X.

[0059] The translation member 233 can be roughly trapezoidal in shape, and the surface of the mounting base 232 facing the translation member 233 is also an inclined surface 2331. When the lifting member 22 drives the mounting base 232 to move upward relative to the bracket 21, because the distance between the inclined surface 2331 of the translation member 233 and the mating member 10 gradually decreases towards the side closer to the stop member 30, the mounting base 232 can apply a force along the second direction Y and toward the elastic member 24 to the translation member 233. As the mounting base 232 rises relative to the bracket 21, the translation member 233 moves continuously toward the direction of pressing the elastic member 24.

[0060] This simplifies the structure of the translation component 233 and reduces the difficulty of its fabrication.

[0061] For more details, please continue reading. Figure 3 In some embodiments, the friction element 23 further includes a rolling element 234 disposed between the mounting base 232 and the inclined surface 2331.

[0062] The rolling element 234 can be, but is not limited to, a roller. When the mounting base 232 moves upward relative to the bracket 21, the rolling friction generated between the mounting base 232 and the roller can drive the roller to roll. When the roller rotates, rolling friction can also be generated between the inclined surface 2331 of the translation element 233.

[0063] This configuration reduces the friction between the mounting base 232 and the inclined surface 2331 without affecting the movement of the translation component 233 along the second direction Y. It converts surface contact into point contact, reduces the wear between the mounting base 232 and the inclined surface 2331, extends the service life of the mounting base 232 and the translation component 233, and reduces the lifting force required by the lifting component 22.

[0064] In some embodiments, the tilt angle formed between the tilted surface 2331 of the translation member 233 and the support 21 is α, the lifting force on the friction element 23 is T, the lifting force includes the lifting force applied by the lifting member 22 to the friction element 23 and the friction force generated between the friction element 23 and the mating member 10, and the pressure applied by the elastic member 24 to the mating member 10 along the second direction Y is P1, where T>P×sinα×cos×α.

[0065] The lifting force can be understood as the sum of two forces: one force is the lifting force provided by the speed limiter, and the other force is the pulling force provided by the friction force formed between the friction element 23 and the mating part 10.

[0066] When the braking device 100 is in a braking state, the lifting member 22 applies an upward pulling force relative to the bracket 21 to the mounting base 232. Under the action of the translation member 233 of the lifting member 22, the mounting base 232 and the damping wheel 231 move closer to the mating member 10, and the damping wheel 231 and the mating member 10 abut against each other. As the mounting base 232 continues to move upward relative to the bracket 21, the mounting base 232 can apply a force in the second direction Y and opposite to the mating member 10 to the translation member 233, thereby driving the translation member 233 to move along the bracket 21 and compress the elastic member 24, and the elastic member 24 can generate an elastic restoring force. As the mounting base 232 continues to move, the translation member 233 also continuously compresses the elastic member 24, and the elastic restoring force generated by the elastic member 24 continuously increases. Because the contact surface between the translation member 233 and the mounting base 232 is an inclined surface 2331, the total force exerted by the elastic member 24 on the translation member 233 can be decomposed into a component force along the first direction X and a component force along the second direction Y.

[0067] Assuming the tilt angle formed between the inclined surface 2331 of the translation member 233 and the support 21 is α, since α is usually small, the component force along the second direction Y applied by the elastic member 24 to the translation member 233 is also small in the initial stage. As the total force applied by the elastic member 24 to the translation member 233 increases, the component force along the second direction Y applied by the elastic member 24 to the translation member 233 also increases.

[0068] For example, such as Figure 3As shown, the elastic restoring force along the second direction Y exerted by the elastic element 24 on the translation element 233 is P1, and the total force exerted by the translation element 233 on the mounting base 232 is P1×cosα. The total force exerted by the translation element 233 on the mounting base 232 and the damping wheel 231 as a whole can be decomposed into a component force T1 along the first direction X and a component force T2 along the second direction Y. Wherein, T1=P1×cosα×sinα, T2=P1×cosα×cosα.

[0069] The total lifting force T on the mounting base 232 is the sum of the pulling force F provided by the frictional force between the damping wheel 231 and the mating part 10, and the lifting force T3 provided by the speed limiter. The pulling force F provided by the frictional force between the damping wheel 231 and the mating part 10 is F = μ × P1 × cosα × cosα, where μ is the static friction coefficient between the damping wheel 231 and the mating part 10. Therefore, T = T3 + μ × P1 × cosα × cosα.

[0070] Because the tilt angle α is small and μ is large, the relationship T>T1 exists. There will never be a situation where the component force T1 is greater than the lifting force T.

[0071] As the elastic element 24 acts on the damping wheel 231, the frictional force between the damping wheel 231 and the mating member 10 gradually increases until the mounting base 232 and the stop member 30 come into contact, at which point the elastic element 24 generates the maximum elastic restoring force. During this process, the damping wheel 231 and the mating member 10 remain relatively stationary. At this point, the elastic element 24 must act on the damping wheel 231 such that the frictional force between the damping wheel 231 and the mating member 10 is greater than the rotational resistance f of the damping wheel 231. Therefore, slippage will not occur between the damping wheel 231 and the mating member 10, reducing the damage to the mating member 10 caused by the operation of the damping wheel 231.

[0072] Furthermore, in some embodiments, the rotational resistance of the damping wheel 231 itself is f, the coefficient of friction between the damping wheel 231 and the mating member 10 is μ, and in the braking state, when the friction element 23 and the stop member 30 abut, the pressure applied by the damping wheel 231 to the mating member 10 in the second direction is P2, where f < μ × P2.

[0073] The outer surface of the damping wheel 231 can be made of a fine-toothed, high-hardness material to maximize the coefficient of friction μ between it and the mating part 10. According to the above formula, if f remains constant, the larger μ is, the smaller P is. Therefore, the size of the elastic element 24 can be reduced, which is beneficial for improving cost-effectiveness. Furthermore, as the number of damping wheels 231 increases, the resistance f of a single damping wheel 231 can be smaller, and the overall pressure P of the damping wheels 231 on the mating part 10 can also be reduced accordingly, resulting in less damage. For example, in… Figure 3In the example shown, the braking device 100 is equipped with two damping wheels 231, which can be increased to four, six, etc., in multiples of two.

[0074] Furthermore, in some embodiments, two braking devices 100 are configured, each equipped with two damping wheels 231. The rotational resistance f of each damping wheel 231 means that the total resistance provided by the damping wheels 231 to the elevator is 4 × f. According to the mechanical formula f = ma, the deceleration of the elevator braking is a = (4f - mg) / m, where m is the mass of the elevator. As can be seen from the formula, the deceleration of the elevator is only related to the elevator mass m and the resistance f of the damping wheels 231, and has little to do with the guide rail, making it suitable for various guide rails.

[0075] It should be noted that the damping wheel 231 can be a wheel equipped with brake pads, and the rotational resistance is achieved through the friction between the brake pads and the wheel. However, it is not limited to a single form; any wheel that can provide its own constant rotational resistance can be the damping wheel 231 in the embodiments of this application.

[0076] like Figure 3 As shown, in some embodiments, the braking mechanism 20 is symmetrically arranged about the mating member 10.

[0077] For example, such as Figure 3 As shown, a braking mechanism 20 is provided on both sides of the mating member 10 along the second direction Y. When the braking force device 100 is running, the two braking mechanisms 20 operate simultaneously, which can improve the braking effect of the braking mechanism 20.

[0078] In addition, this application also provides an elevator. This elevator includes the braking device 100 from any of the above embodiments. For details regarding the braking device 100, please refer to the relevant description above; it will not be repeated here.

[0079] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0080] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A braking force device, characterized in that, include: The dual component extends along the first direction; A braking mechanism is provided on at least one side of the mating member along the first direction. The braking mechanism includes a bracket, a lifting member, a friction element, and an elastic element. The lifting member, the friction element, and the elastic element are located within the bracket. One end of the friction element is connected to the lifting member, and the other end is movably connected to the elastic element. The friction element is provided between the mating member and the elastic element along a second direction, which intersects with the first direction. When in a braking state, the friction element moves relative to the bracket in the first direction under the action of the lifting member, can roll and abut against the mating member, and compresses the elastic element in the second direction. The elastic element applies a force to the friction element in the first direction and the second direction. The braking device further includes a stop member, which is disposed above the friction element in the first direction. Before the friction element and the stop member come into contact, the damping wheel of the friction element can come into contact with the mating member and remain stationary relative to the mating member. When in the braking state, the damping wheel and the mating member roll and abut against each other; when in the normal state, the damping wheel and the mating member are spaced apart.

2. The braking device according to claim 1, characterized in that, The friction element includes the damping wheel and the mounting base. The mounting base is connected to the lifting member and the elastic member. The damping wheel and the mounting base are rotatably connected and located between the mounting base and the mating member.

3. The braking device according to claim 2, characterized in that, The friction element further includes a translation member, one end of which is movably connected to the mounting base, and the other end of which is connected to the elastic member. In the second direction, the translation member can move along the bracket and compress the elastic member.

4. The braking force device according to claim 3, characterized in that, The translation member has an inclined surface facing the mating member, and the distance between the inclined surface and the mating member gradually increases from the end where the stop member is located along the first direction.

5. The braking device according to claim 4, characterized in that, The friction element further includes a rolling element disposed between the mounting base and the inclined surface.

6. The braking device according to claim 4, characterized in that, The tilt angle formed between the inclined surface of the translation member and the support is α, the lifting force on the friction element is T, the lifting force includes the lifting force applied by the lifting member to the friction element and the friction force generated between the friction element and the mating member, the pressure applied by the elastic member to the mating member along the second direction is P1, where T>P1×sinα×cosα.

7. The braking device according to claim 6, characterized in that, The rotational resistance of the damping wheel itself is f, and the sliding friction coefficient between the damping wheel and the mating member is μ. In the braking state, when the friction element and the stop member abut, the pressure applied by the damping wheel to the mating member along the second direction is P2, where f < μ × P2.

8. The braking device according to any one of claims 1-7, characterized in that, The braking mechanism is symmetrically arranged about the pair of components.

9. An elevator, characterized in that, The elevator includes the braking device as described in any one of claims 1-8.

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