Braking force device and elevator

Abstract

The invention relates to a braking force device and an elevator. The braking force device comprises a mating plate and a braking mechanism. The mating plate extends along a first direction; the braking mechanism is arranged on at least one side of the mating plate in the first direction and comprises a support, a lifting part, a friction element and an elastic part, the lifting part, the friction element and the elastic part are located in the support, one end of the friction element is connected with the lifting part, the other end of the friction element is movably connected with the elastic part, and the friction element is arranged between the mating plate and the elastic part in the second direction. The second direction intersects with the first direction; in the braking state, the friction element moves in the first direction relative to the support under the action of the lifting part, can abut against the mating plate in a rolling mode and compresses the elastic part in the second direction, and the elastic part exerts acting force on the friction element in the first direction and the second direction. When the braking force device is in the braking state, the friction element runs in a rolling mode relative to the mating plate, the mating plate is not damaged, and the braking force is determined by the friction element.

Description

Technical Field

[0001] The present application relates to the technical field of elevator braking, and in particular to a braking force device and an elevator. Background Art

[0002] The brake force device is an important device in the elevator equipment and an important component of the elevator's safety protection function. It is generally installed at the lower part of both sides of the elevator car. When the elevator overspeeds or falls in a fault state and the speed reaches the speed of the speed limiter, the speed limiter operates the brake force device to stop the elevator car safely and clamp it on the dual part to avoid accidents. The safety factor of the elevator is higher.

[0003] Due to the differences in the processing methods, surface protection, working conditions, processing and manufacturing errors of the mating parts, or the influence of external factors such as rust and oil, the change of friction factors will exist in a large range, resulting in the inability of traditional braking force devices to meet the safe stopping conditions under all working conditions, seriously affecting the braking capacity. Especially in the elevator reconstruction market, the conditions of the original old elevators and old mating parts are even more diverse, and it is impossible to conduct a one-to-one matching test. The rash selection of safety clamps is likely to lead to the risk of being unable to stop the elevator.

[0004] However, the braking force device currently using sliding friction braking usually causes scratches on the mating parts during use. As the number of times the braking force device is used increases, the degree of damage to the mating parts increases. Damaged mating parts can cause a serious decline in braking performance, affecting elevator safety.

[0005] Therefore, there is an urgent need for a braking device that causes less damage to the paired parts, and the braking force of the braking device is not affected by changes in the friction factors of the paired parts. Summary of the invention

[0006] Based on this, it is necessary to provide a braking force device and an elevator to address the problem that the braking force device causes severe wear of the dual parts during operation, which affects the service life of the dual parts, and the change of friction factors of different dual parts causes unstable braking force.

[0007] A braking force device, comprising:

[0008] A dual member extending along a first direction;

[0009] a brake mechanism, arranged on at least one side of the pair of members along the first direction, the brake mechanism comprising a bracket, a lifting member, a friction element and an elastic member, the lifting member, the friction element and the elastic member are located in the bracket, one end of the friction element is connected to the lifting member, and the other end is movably connected to the elastic member, the friction element is arranged between the pair of members and the elastic member along a second direction, and the second direction intersects with the first direction;

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

[0011] In one embodiment, the braking force device further includes a stopper, which is disposed above the friction element in the first direction, and before the friction element and the stopper abut against each other, the damping wheel of the friction element can abut against the counterpart and remain stationary relative to the counterpart.

[0012] In one embodiment, the friction element includes the damping wheel and a mounting seat, the mounting seat is connected to the lifting member and the elastic member, the damping wheel is rotatably connected to the mounting seat, and is located between the mounting seat and the dual member;

[0013] When in the braking state, the damping wheel and the mating member are in rolling contact; 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 seat, 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 squeeze the elastic member.

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

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

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

[0018] In one embodiment, the rotational resistance of the damping wheel itself is f, the friction coefficient between the damping wheel and the dual member is μ, and in the braking state, when the mounting seat and the stop member abut against each other and the elastic member is deformed, the pressure applied by the damping wheel on the dual member along the second direction is P2, f<μ×P2.

[0019] In one of the embodiments, the braking mechanism is symmetrically arranged with respect to the dual member.

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

[0021] In the above-mentioned braking force device and elevator, when the braking force device is in a braking state, the friction element can approach and act on the dual part under the joint action of the lifting member and the elastic member. Moreover, during the entire operation process, the friction element will be stationary relative to the dual part at the beginning. After the friction element and the stopper abut, the damping wheel can rotate and generate rolling friction. Therefore, the wear on the dual part is small and will not affect the service life of the dual part. Since the damping wheel will rotate until the elevator stops, the resistance encountered by the elevator from the rotation of the damping wheel to the stop comes from the rotation resistance of the damping wheel itself, which is not affected by the dual part and can provide a stable braking force. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 A schematic diagram of the structure of the braking force device provided in some embodiments of the present application when it is in a normal state.

[0023] Figure 2 A schematic diagram of the structure in which the braking force device provided in some embodiments of the present application is in a braking state but the elastic member is not squeezed.

[0024] Figure 3 A schematic diagram of the structure in which the braking force device provided in some embodiments of the present application is in a braking state but the elastic member is squeezed.

[0025] Description of reference numerals:

[0026] 100. Braking device;

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

[0028] X, first direction; Y, second direction. DETAILED DESCRIPTION

[0029] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0030] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0031] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0032] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0033] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being “above”, “above”, and “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below”, and “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0034] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and are not intended to be the only implementation method.

[0035] See also Figures 1 to 3 Some embodiments of the present application provide a braking force device 100. The braking force device 100 includes a dual member 10 and a braking mechanism 20. The dual member 10 extends along a first direction X; the braking mechanism 20 is arranged on at least one side of the dual member 10 along the first direction X, and the braking mechanism 20 includes a bracket 21, a lifting member 22, a friction element 23 and an elastic member 24, the lifting member 22, the friction element 23 and the elastic member 24 are located in 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 member 24, and the friction element 23 is arranged between the dual member 10 and the elastic member 24 along a second direction Y, and the second direction Y intersects with the first direction X.

[0036] In the braking state, the friction element 23 moves relative to the bracket 21 along the first direction X under the action of the lifting member 22, can roll and abut with the dual member 10, and compress the elastic member 24 along 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 is described below in conjunction with an application scenario in which the braking force device 100 is applied to an elevator car.

[0038] See also Figure 1 The dual member 10 is extended along a first direction X, and the elevator car can move relative to the dual member 10 along the first direction X. The first direction X here can be understood as a vertical direction.

[0039] The braking device 100 is movably installed at the lower part of the elevator car. When the running speed of the elevator is within the normal range, the braking device 100 is in a normal state, and the friction element 23 and the mating member 10 are not in contact. When the elevator car descends at an overspeed, the braking device 100 switches from the normal state to the braking state, and the braking device 100 starts to operate.

[0040] The specific operation process of the braking force device 100 is as follows: the speed limiter installed on the car can apply an upward pulling force to the lifting member 22. Driven by the lifting member 22, the friction element 23 begins to be stationary relative to the dual member 10 in the first direction X. As the elevator car continues to descend, the bracket 21 is driven to move downward. Since the friction element 23 is subjected to the upward pulling force of the lifting member 22, the friction element 23 can gradually approach the dual member 10 and abut against the dual member 10.

[0041] When the friction element 23 and the mating member 10 are in contact, the friction element 23 is driven by the pulling force applied by the lifting member 22 to be stationary relative to the mating member 10 in the first direction X. When the bracket 21 continues to move downward relative to the friction element 23, the friction element 23 squeezes 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, and the second direction Y is perpendicular to the first direction X. At this time, the force along the second direction Y applied by the elastic member 24 to the friction element 23 can be understood as the horizontal direction in the figure.

[0042] During the downward movement of the bracket 21 relative to the friction element 23, the compression degree of the elastic member 24 gradually intensifies, the elastic restoring force generated by the elastic member 24 gradually increases, and the force applied to the friction element 23 also gradually increases. If the sum of 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 dual member 10 is greater than the downward thrust given to the friction element 23 by the elastic member 24, the friction element 23 remains stationary relative to the dual member 10. When the friction element 23 and the bracket 21 are in contact, the friction element 23 and the bracket 21 no longer move relative to each other along the first direction X, and the braking force device 100 completes the braking deformation operation. Subsequently, the part of the friction element 23 that can roll and contact with the dual member 10 begins to operate. For example, the damping wheel 231 of the friction element 23 begins to rotate and generates its own rotational resistance, and begins to formally provide braking force for the elevator to stop the elevator. In this process, because the friction element 23 is in rolling contact with the counterpart 10 , the counterpart 10 is less worn, and the force providing deceleration for the elevator car comes from the self-rotational resistance f generated by the damping wheel 231 .

[0043] In summary, when the braking device 100 is in a braking state, the friction element 23 can approach and act on the mating part 10 under the joint action of the lifting member 22 and the elastic member 24. In addition, during the entire operation process, the friction element 23 is in rolling contact with the mating part 10, so the wear on the mating part 10 is small and the service life of the mating part 10 is not affected.

[0044] The dual member 10 in the embodiment of the present application can be understood as a guide rail structure in an elevator. Due to different processing methods, surface protection, working conditions, processing and manufacturing errors, or factors such as rust and oil, the friction coefficient on the dual member 10 can vary within a large range. Therefore, the traditional braking force device 100 cannot meet the design of the dual member 10 under different working conditions and cannot guarantee a constant braking force. For this reason, the introduction of the braking force device 100 of the present application can effectively meet the design of different friction coefficients and ensure a constant braking force.

[0045] In some embodiments, the braking force device 100 also includes a stopper 30, which is arranged above the friction element 23 in the first direction X. Before the friction element 23 and the stopper 30 abut against each other, the damping wheel 231 of the friction element 23 can abut against the dual member 10 and remain stationary relative to the dual member 10.

[0046] The structure of the stopper 30 may be, but is not limited to, a block shape, and the stopper 30 may be disposed on the bracket 21, and the number of the stopper 30 may correspond to the number of the mounting seats 232. That is, one mounting seat 232 is equipped with one stopper 30. A channel may be reserved between the stopper 30 and the mating member 10 for the lifting member 22 to run.

[0047] In the initial stage of the braking state, the mating member 10 and the friction element 23 are in a relatively static state. When the lifting member 22 drives the friction element 23 to move upward relative to the bracket 21, the damping wheel 231 of the friction element 23 first contacts the mating member 10. At this time, there is still a distance between the friction element 23 and the stopper 30. As the lifting member 22 operates, the friction element 23 continues to move upward relative to the bracket 21, and the friction element 23 is gradually subjected to an increasing force from the elastic member 24 until the friction element 23 contacts the stopper 30, and the braking force device 100 completes the braking deformation operation.

[0048] When the friction element 23 and the stopper 30 are in contact, the bracket 21 will continue to move downward, and then the damping wheel 231 of the friction element 23 starts to rotate and generates its own rotational resistance. In this way, the braking force device 100 begins to formally provide braking force for the elevator car to stop the elevator. In this process, because the friction element 23 is in rolling contact with the dual part 10, the dual part 10 is less worn, and the force that provides deceleration for the elevator comes from the self-rotational resistance generated by the damping wheel 231. It should be noted that because the damping wheel 231 can roll relative to the dual part 10, the deceleration resistance when the elevator car descends mainly depends on the resistance of the damping wheel 231.

[0049] In this way, the friction element 23 can be limited by setting the stopper 30, and the distance that the damping wheel 231 of the friction element 23 abuts against the mating part 10 and moves relative to the mating part 10 is controlled, so that the wear amount of the mating part 10 can be reduced.

[0050] In some embodiments, the friction element 23 includes a damping wheel 231 and a mounting seat 232, the mounting seat 232 is connected to a lifting member 22 and an elastic member 24, the damping wheel 231 and the mounting seat 232 are rotatably connected, and are located between the mounting seat 232 and the dual member 10; when in a braking state, the damping wheel 231 and the dual member 10 are in rolling contact; when in a normal state, the damping wheel 231 and the dual member 10 are spaced apart.

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

[0052] During the process of the braking force device 100 switching from the normal state to the braking state, the damping wheel 231 and the mounting seat 232, driven by the lifting member 22, continuously approach the direction of the dual member 10. After the damping wheel 231 abuts against the dual member 10, the mounting seat 232 abuts against the stopper 30. During this process, the elastic member 24 is always in a squeezed state, and the elastic member 24 can apply a force to the mounting seat 232 and the damping wheel 231, so that the damping wheel 231 can have a sufficient positive pressure P with the dual member 10 under the action of the force, ensuring that the sum of 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 dual member 10 is greater than the downward thrust of the elastic member 24 on the friction element 23, so that before the mounting seat 232 abuts against the stopper 30, the damping wheel 231 and the dual member 10 can maintain a relatively static state.

[0053] The friction element 23 is provided with a damping wheel 231 and a mounting seat 232 , so that the friction element 23 can roll relative to the mating member 10 on the basis of simplifying the structure of the friction element 23 .

[0054] Furthermore, if 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 seat 232, and the other end is connected to the elastic member 24. In the second direction Y, the translation member 233 can move along the bracket 21 and squeeze the elastic member 24.

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

[0056] When the lifting member 22 drives the mounting seat 232 to move upward relative to the bracket 21, the mounting seat 232 can drive the translation member 233 to move along the bracket 21 in the direction of continuously squeezing the elastic member 24, so that the elastic member 24 is deformed and generates elastic restoring force. Before the deformation of the elastic member 24 reaches the maximum value, the mounting seat 232 and the stopper 30 are completely in contact with each other. At this time, the force exerted by the elastic member 24 on the mounting seat 232 and the damping wheel 231 reaches the maximum.

[0057] The above arrangement utilizes the mounting seat 232 that moves along the first direction X relative to the bracket 21 to drive the translation member 233 to move along the second direction Y to squeeze the elastic member 24, thereby realizing linkage movement along two different directions and simplifying the method of driving the elastic member 24 to move along the second direction Y.

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

[0059] The shape of the translation member 233 can be roughly trapezoidal, and the surface of the mounting seat 232 facing the translation member 233 is also a tiltable surface 2331. When the lifting member 22 drives the mounting seat 232 to move upward relative to the bracket 21, because the distance between the tilted surface 2331 of the translation member 233 and the mating member 10 gradually decreases toward the side close to the stop member 30, the mounting seat 232 can exert a force on the translation member 233 along the second direction Y and toward the elastic member 24. As the mounting seat 232 continues to rise relative to the bracket 21, the translation member 233 continues to move in the direction of squeezing the elastic member 24.

[0060] In this way, the structure of the translation member 233 is simplified, and the difficulty of manufacturing the translation member 233 is reduced.

[0061] For more details, please refer to Figure 3 In some embodiments, the friction element 23 further includes a rolling member 234 , and the rolling member 234 is disposed between the mounting seat 232 and the inclined surface 2331 .

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

[0063] Such a configuration can reduce the friction force generated between the mounting seat 232 and the inclined surface 2331 without affecting the movement of the translation member 233 along the second direction Y, convert the surface contact into point contact, and reduce the wear between the mounting seat 232 and the inclined surface 2331, thereby extending the service life of the mounting seat 232 and the translation member 233 and reducing the lifting force required by the lifting member 22.

[0064] In some embodiments, the inclination angle formed between the inclined surface 2331 of the translation member 233 and the bracket 21 is α, the lifting force exerted 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 dual member 10, and the pressure along the second direction Y applied by the elastic member 24 to the dual member 10 is P1, wherein T>P×sinα×cos×α.

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

[0066] When the braking force device 100 is in a braking state, the lifting member 22 applies an upward pulling force to the mounting seat 232 relative to the bracket 21, and the mounting seat 232 and the damping wheel 231 approach the dual member 10 under the action of the translation member 233 of the lifting member 22, and the damping wheel 231 abuts against the dual member 10. As the mounting seat 232 continues to move upward relative to the bracket 21, the mounting seat 232 can apply a force in the second direction Y and in the opposite direction of the dual member 10 to the translation member 233, thereby driving the translation member 233 to move along the bracket 21 and squeeze the elastic member 24, and the elastic member 24 can generate an elastic restoring force. As the mounting seat 232 continues to move, the translation member 233 also continuously squeezes the elastic member 24, and the elastic restoring force generated by the elastic member 24 continues to increase. Because the contact surface between the translation member 233 and the mounting seat 232 is the inclined surface 2331 , the total force applied by the elastic member 24 to the translation member 233 can be decomposed into a force component along the first direction X and a force component along the second direction Y.

[0067] Assuming that the inclination angle formed between the inclined surface 2331 of the translation member 233 and the bracket 21 is α, because 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 continues to increase, the component force along the second direction Y applied by the elastic member 24 to the translation member 233 also increases accordingly.

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

[0069] The total pulling force T on the mounting seat 232 is the sum of the pulling force F provided by the friction force formed between the damping wheel 231 and the dual member 10 and the pulling force T3 provided by the speed limiter. The pulling force F provided by the friction force formed between the damping wheel 231 and the dual member 10 = μ × P1 × cos α × cos α, where μ is the static friction coefficient of the damping wheel 231 and the dual member 10. Therefore, T = T3 + μ × P1 × cos α × cos α.

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

[0071] As the elastic member 24 acts on the damping wheel 231, the friction force generated between the damping wheel 231 and the mating member 10 gradually increases until the mounting seat 232 and the stopper 30 abut against each other, and the elastic member 24 generates an elastic restoring force of maximum force. During this process, the damping wheel 231 and the mating member 10 remain in a relatively static state. At this time, the elastic member 24 is required to act on the damping wheel 231 so that the friction force generated between the damping wheel 231 and the mating member 10 is greater than the self-rotation resistance f of the damping wheel 231. Therefore, there will be no slipping between the damping wheel 231 and the mating member 10, which can reduce the damage caused to the mating member 10 by the damping wheel 231 during operation.

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

[0073] The outer wheel surface of the damping wheel 231 can be made of a fine-toothed high-hardness material to maximize the friction coefficient μ between the damping wheel 231 and the mating part 10. According to the above formula, if f remains unchanged, the larger μ is, the smaller P is. Therefore, the elastic part 24 specification of the elastic part 24 can be reduced, which is beneficial to improving the cost performance. In addition, when 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 wheel 231 on the mating part 10 can also be correspondingly reduced, and the damage is also smaller. For example, in Figure 3In the example shown, the braking force device 100 is equipped with two damping wheels 231 , but the number of damping wheels 231 may be increased in multiples of two to four, six, etc.

[0074] Furthermore, in some embodiments, two sets of braking force devices 100 are configured, and each set of braking force devices 100 is provided with two damping wheels 231. The rotation resistance of each damping wheel 231 is f, so the total resistance that the damping wheel 231 can provide for 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. It can be seen from the formula that the deceleration of the elevator is only related to the mass m of the elevator and the resistance f of the damping wheel 231, and has basically nothing to do with the guide rail, and is suitable for a variety of guide rails.

[0075] It should be noted that the damping wheel 231 can be in the form of a wheel equipped with a brake pad, and the rotation resistance is achieved by the friction between the brake pad and the wheel. However, it is not limited to a single form, and any wheel that can provide its own constant rotation resistance can be the damping wheel 231 in the embodiment of the present application.

[0076] like Figure 3 As shown, in some embodiments, the braking mechanism 20 is symmetrically arranged with respect to the counterpart 10 .

[0077] For example, Figure 3 As shown, a brake mechanism 20 is provided on both sides of the dual member 10 along the second direction Y. When the braking force device 100 is in operation, the two brake mechanisms 20 are operated simultaneously, which can improve the braking effect of the brake mechanism 20.

[0078] In addition, the present application also provides an elevator. The elevator includes the braking force device 100 in any of the above embodiments. For the braking force device 100, please refer to the relevant contents recorded above, which will not be repeated here.

[0079] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described 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 above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be construed as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent application shall be subject to the attached claims.

Claims

1. A braking force device, It is characterized in that include: A dual member extending along a first direction; a brake mechanism, arranged on at least one side of the pair of members along the first direction, the brake mechanism comprising a bracket, a lifting member, a friction element and an elastic member, the lifting member, the friction element and the elastic member are located in the bracket, one end of the friction element is connected to the lifting member, and the other end is movably connected to the elastic member, the friction element is arranged between the pair of members and the elastic member along a second direction, and the second direction intersects with 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, can roll and abut against the mating member, and compress the elastic member along the second direction, and the elastic member applies a force to the friction element in the first direction and the second direction.

2. The braking device according to claim 1, It is characterized in that The braking force device further includes a stopper, which is disposed above the friction element in the first direction. Before the friction element and the stopper abut against each other, the damping wheel of the friction element can abut against the counterpart and remain stationary relative to the counterpart.

3. The braking device according to claim 2, It is characterized in that The friction element comprises the damping wheel and a mounting seat, the mounting seat is connected to the lifting member and the elastic member, the damping wheel is rotatably connected to the mounting seat, and is located between the mounting seat and the dual member; When in the braking state, the damping wheel and the mating member are in rolling contact; when in the normal state, the damping wheel and the mating member are spaced apart.

4. The braking device according to claim 3, It is characterized in that The friction element further comprises a translation member, one end of which is movably connected to the mounting seat, 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 squeeze the elastic member.

5. The braking device according to claim 4, It is 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 along the first direction starting from the end where the stop member is located.

6. The braking device according to claim 5, It is characterized in that The friction element further includes a rolling element, and the rolling element is arranged between the mounting seat and the inclined surface.

7. The braking device according to claim 5, It is characterized in that The inclination angle formed between the inclined surface of the translation member and the bracket is α, the lifting force applied to the friction element is T, the lifting force includes the lifting force applied by the lifting member on the friction element and the friction force generated between the friction element and the dual member, and the pressure applied by the elastic member on the dual member along the second direction is P1, wherein T>P1×sinα×cosα.

8. The braking device according to claim 7, It is characterized in that The rotational resistance of the damping wheel itself is f, the sliding friction coefficient between the damping wheel and the mating part is μ, and in the braking state, when the friction element abuts against the stopper, the pressure along the second direction applied by the damping wheel to the mating part is P2, f<μ×P2.

9. The braking device according to any one of claims 1 to 8, It is characterized in that The braking mechanism is symmetrically arranged with respect to the dual member.

10. An elevator, It is characterized in that The elevator comprises the braking force device according to any one of claims 1-9.

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