Mechanical brake roller door machine assembly

Abstract

The application provides a mechanical brake roller shutter door machine assembly, a brake device of the roller shutter door machine comprises a rotation-stopping part and a set of more than one limited rotation part group, the limited rotation part group comprises an input clutch and an output clutch, at least one of the output clutch and the input clutch is provided with a brake part, the maximum angle cmax of relative rotation of the input clutch and the output clutch is ∈(0, ∞), at least one of the input clutch and the output clutch is provided with a reset mechanism, so that when the input clutch and the output clutch relatively rotate, the rotation angle c has a rotation trend of recovering to 0; the brake device is further provided with a brake delay mechanism, so that after the input clutch and the output clutch reversely relatively rotate, at least in a time period with a time length t greater than 0, the brake delay mechanism acts on the reset mechanism or the output clutch or the input clutch, so that in the relative rotation process of the clutch output part and the clutch input part, the brake part and the rotation-stopping part do not interact.

Description

Technical Field

[0001] This invention relates to the field of electric roller shutter door operators, and more particularly to a clutch and brake device for roller shutter operators. Background Technology

[0002] In the field of roller shutter doors (or simply roller shutter doors), general-purpose electromagnets are used as clutch components for braking. The main reason why mechanical brakes (such as the explosion-proof roller shutter door opening and closing mechanism in application number CN03214561.6) are difficult to widely use in this field is that mechanical brakes must simultaneously meet the following scenario requirements:

[0003] (1) When the door moves upward, most mechanical self-locking mechanisms can handle it. During this stage, the output end of the brake device always rotates in the opposite direction to gravity, and the torque vector direction of the brake input end to the output end is in the same direction as the rotation direction of the output end (the force and gravity are always opposite). When the motor is de-energized, the door body rotates in the opposite direction by its own weight. Therefore, as long as the self-locking mechanism has a reversing function, it can achieve this technical goal.

[0004] (2) When the door moves downward, if the action of the braking mechanism and the internal resistance of the roller shutter system (such as friction, possible mechanical interference, etc.) are not considered, the output end of the braking device always rotates in the same direction as gravity, and the torque vector direction of the brake input end to the output end is opposite to the rotation direction of the output end (the force and gravity are always opposite); however, the explosion-proof roller shutter opening and closing machine of application number CN03214561.6 has several problems in this stage:

[0005] 1) Unable to descend continuously at the predetermined speed;

[0006] 2) It is prone to continuous impact noise;

[0007] 3) The service life of braking devices is significantly reduced compared to other fields.

[0008] The root cause of the above problems is that the complex and dynamic factors such as the gradual increase in gravity as the length of the drooping door increases during the descent, and the transformation from "the weight of the drooping door being less than the internal resistance of the mechanism" to "the weight of the drooping door being greater than the internal resistance of the mechanism" were not taken into account.

[0009] In addition, traditional mechanical brakes rely on friction pads, requiring the spring force of the reset mechanism to generate sufficient friction. When the extended door body is short, the gravity is small, which can easily lead to frequent accidental braking, whether going up or down. Summary of the Invention

[0010] Purpose of the invention:

[0011] Against this backdrop, the present invention proposes to divide the door's downward movement into two stages: the process of disengaging from the self-locking position and the process after disengaging from the self-locking position. It also provides a purely mechanical brake roller shutter door motor to achieve adaptive coordination of the two stages in the downward movement of the roller shutter door driven by the motor.

[0012] To achieve the above objectives, the overall technical solution provided by this invention is as follows:

[0013] A mechanical brake roller shutter door motor assembly, comprising a motor, a motor operation control circuit, a braking device, and a gearbox, wherein the output shaft of the motor drives and connects to the gearbox, the output component of the gearbox drives and connects to the roller shutter door's rollers, and the braking device is connected to a transmission system consisting of the motor output shaft and the roller input component; characterized in that: the braking device includes an anti-rotation part and one or more sets of limited rotation components, each set of limited rotation components including a clutch input component and a clutch output component, at least one of the clutch output component and the clutch input component being provided with or drivenly connected to a braking part, the clutch input component being drivenly connected to the clutch output component, and the maximum relative rotation angle c between the clutch input component and the clutch output component. max The absolute value of the clutch input and clutch output components is greater than 0 and less than infinity. At least one of these components is provided with a reset mechanism, ensuring that when the relative rotation angle c between the clutch input and clutch output components is not 0, the clutch input and clutch output components tend to return to a rotation angle c of 0. The braking device also includes a braking delay mechanism, ensuring that after the clutch input and clutch output components undergo opposite relative rotation, for at least a time period t greater than 0, the braking delay mechanism acts on the reset mechanism, the clutch output component, or the clutch input component, satisfying that during the relative rotation of the clutch output and clutch input components, the braking part and the anti-rotation part do not interact to achieve braking. Furthermore, the braking delay mechanism satisfies that the rotation time T between the clutch input and clutch output components from the relative rotation limit state in one direction to the relative rotation limit state in the other direction is less than t.

[0014] (a) Regarding the braking device / one-way drive mechanism formed by the combination of clutch input component, clutch output component, and anti-rotation component, the present invention provides the following two solutions.

[0015] Option ii: The clutch input component is an input axial cam, and the clutch output component is an output axial cam; the input axial cam and the output axial cam abut against each other, and when the input axial cam and the output axial cam rotate relative to each other, at least one of the input axial cam and the output axial cam undergoes axial movement, causing the braking part to extend into or disengage from the anti-rotation part; the input axial cam is fixedly or rotatably mounted on the transmission component above the input axial cam in the transmission system (rotatable, but not infinitely rotatable, e.g., rotatable from 0° to 720°), and the output axial cam is axially movable and mounted on the transmission component below the output axial cam in the transmission system;

[0016] Scheme i-ii: The clutch input component is an input radial cam, and the clutch output component is an output radial cam; the input radial cam and the output radial cam abut against each other, and when the input radial cam and the output radial cam rotate relative to each other, at least one of the input radial cam and the output radial cam rotates by a limited angle, causing the braking part to act or disengage from the anti-rotation part; the input radial cam is fixedly or rotatably fitted onto the transmission component above the input radial cam in the transmission system (rotatable, but not infinitely rotatable, e.g., rotatable from 0° to 720°), and the output radial cam is axially movable and fitted onto the transmission component below the output radial cam in the transmission system.

[0017] (II) Regarding the braking delay mechanism, the present invention provides the following two solutions, which can be selected or used simultaneously.

[0018] Solution ii-i: The brake delay mechanism has a brake delay space between the anti-rotation part and the braking part. When the clutch output part and the clutch input part rotate in opposite directions, the reset mechanism cannot drive the braking part to immediately act on the anti-rotation part for at least a period of time. That is, the anti-rotation part and the braking part can only interact after the clutch output part and the clutch input part rotate in opposite directions at a non-0° angle.

[0019] Solution ii-ii: The braking delay mechanism includes a circumferential buffer provided in the anti-rotation part and / or the braking part, so that when the anti-rotation part and the braking part interact, they continue to rotate or swing at a non-zero angle before completing the braking.

[0020] (III) Regarding the reset mechanism, the present invention provides the following four solutions, one of which can be selected or used simultaneously.

[0021] Scheme iii-i: The reset mechanism includes one or more elastic elements, and has the following characteristics: the natural length of the elastic element is less than the axial length of the space in which the elastic element can move when the braking part is furthest from the anti-rotation part;

[0022] Scheme iii-ii: The braking part has elastic elements respectively provided along the axial direction on the front and rear end faces;

[0023] Option iii-iii: The reset mechanism includes one or more magnetic components (e.g., permanent magnets);

[0024] Scheme iii-v: The next stage of transmission in the transmission system for the clutch output component is a transition wheel; the reset mechanism has a counter-pressure protrusion on one component and inclined baffles on both sides of the counter-pressure protrusion on the other component, at a position close to the clutch output component and the transition wheel; the inclined baffles face the anti-rotation part, so that when the transition wheel drives the clutch output component to rotate relatively clockwise or relatively counterclockwise, the clutch output component will be displaced towards the anti-rotation part.

[0025] Furthermore, in the aforementioned four schemes, the braking part is provided with an electromagnet on the front and rear end faces along the axial direction at the other end relative to the reset mechanism; furthermore, the magnet is a magnetic conductive component connected to the motor shaft (because the force required for the reset mechanism to achieve reset in this invention is much smaller than that in traditional products, the rotor of the AC motor has magnetic force when energized, which can overcome the reset tendency of the reset mechanism, thereby achieving no false braking when energized).

[0026] (iv) Optimization measures for the overall technical solution. The following optimization measures are introduced using solution ii from point (i) as an example:

[0027] Optimization measure (A): When both scheme iii-i and scheme iii-v are used simultaneously, a moving track with the counter-pressure protrusion is provided axially between the two inclined baffles; the inclined baffles face the anti-rotation part, so that when the transition wheel drives the clutch output part to rotate relatively clockwise or relatively counterclockwise, the clutch output part will be axially displaced in the direction closer to the anti-rotation part.

[0028] Furthermore, the connection between the baffle and the track is located inside the anti-rotation part.

[0029] Optimization measure (B): The anti-rotation part includes two or more anti-rotation components, which are fixed on the motor end cover; when braking, the braking part acts on at least two anti-rotation components simultaneously.

[0030] Optimization measure (C): One of the input axial cam and the output axial cam is provided with positive and negative threaded grooves or threaded holes, and the other component is provided with a synchronous protrusion, so that when the relative rotation angle of the input axial cam and the output axial cam changes, the mutual axial distance (axial position of the braking part) changes.

[0031] Optimization measure (D): When the braking part is disengaged from the anti-rotation part, the force exerted by the reset mechanism on the clutch input and clutch output components is less than the force exerted by the clutch input on the clutch output. [For example: Let the angle between the inclined plane of the inclined baffle and the axial direction be x, and the angle between the contact surfaces of the clutch input and clutch output components and the axial direction be y, then tan(y) ≥ tan(x) or y ≥ x].

[0032] The advantages of the above technical solution are:

[0033] 1. This invention connects one or more unidirectional drive mechanisms in series with a brake delay mechanism in the transmission system. During the downward movement of the door driven by the motor, it effectively prevents the door from accidentally braking by having the brake part re-interact with the anti-rotation part after disengaging from the anti-rotation part through the transmission system. Specifically, the unidirectional drive mechanism enables the motor to drive the transmission system in one direction, meaning the motor output shaft is the sole drive source. When the roller shutter door is the only power source, the transmission system brakes. In other words, when the motor loses power (power failure and no manual operation of the chain), and the gearbox's power source is solely the roller shutter door, the transmission system's power in the permissible transmission direction is interrupted, and braking occurs. The unidirectional drive mechanism is provided with one or more sets of finite rotating parts, each set including a clutch input and a clutch output. The clutch input is connected to the clutch output, and the absolute value of the relative rotation angle between the clutch input and the clutch output is greater than 0 and less than infinity. The upper-level transmission component of the clutch input provides power drive (excluding braking) to the clutch input. Since the lower-level transmission component of the clutch output always provides power input to the clutch output, the clutch input and the clutch output rotate relative to each other, releasing the braking state. A reset mechanism is provided between the clutch input and the clutch output, so that when the clutch input and the clutch output are disengaged from their default state, the anti-rotation part and the braking part of the brake assembly tend to move closer to each other, such as making the braking part tend to extend into the anti-rotation part when it is disengaged from the anti-rotation part.

[0034] 2. The braking device of the present invention is connected in series in the transmission system. At least one of the input axial cam and the output axial cam can undergo axial displacement and cannot disengage from the mutually inserted state. When the motor output shaft drives the gearbox input shaft to rotate asynchronously (whether forward or reverse), at least one cam in the unidirectional drive mechanism undergoes axial displacement and can drive the output axial cam to rotate synchronously after rotating a certain angle c, thereby driving the door body to move up or down. When the driving force (torque) of the motor on the output axial cam through the input axial cam is less than or equal to the torque formed by the maximum rotational inertia of the motor rotor when the power is off (this specified value is inaccurate if it is "the torque of the roller shutter door on the output axial cam through the transmission system", because during the downward movement, the motor only prevents the door body from falling freely, but the total movement is still downward, that is, the motor torque may be less than the gravitational torque), after the braking part rotates a certain angle, it interacts with the anti-rotation part to brake.

[0035] 3. The reset mechanism of the brake device of the present invention is provided with a mechanism for synchronously changing the rotational and axial movement states of the input axial cam and the output axial cam (e.g., the cooperation between the counter-pressure protrusion and the inclined baffles on both sides). When the relative rotation angle of the input axial cam and the output axial cam changes, their axial distance (axial position of the brake part) changes synchronously. This achieves the following: when the motor is energized (the input axial cam has a load output state), during the change in the relative rotation direction of the input axial cam and the output axial cam, the brake part cannot extend into the anti-rotation part or the brake part moves away from the anti-rotation part before braking occurs.

[0036] 4. The braking device of the present invention is provided with a counter-pressure cam group (applicable to all schemes) at the end of the movement track of the braking part towards the anti-rotation part, so as to realize that the braking is made deeper into the anti-rotation part by the weight of the roller shutter door, effectively preventing the roller shutter door from falling out of the limit of the anti-rotation part due to excessive weight.

[0037] 5. The elastic element described in this invention has a natural length less than the axial length of the space in which the elastic element can move when the braking part is furthest from the anti-rotation part, and / or the braking part has the elastic element respectively arranged axially on the front and rear end faces. This not only effectively reduces the impact noise of the braking part when the reset mechanism is activated, but also reduces the force required for the motor output shaft to drive the braking part to disengage from the anti-rotation part. This technical solution is based on the premise of a counter-pressure cam assembly; otherwise, it is easy to lead to the risk of brake failure. Attached Figure Description

[0038] Figure 1 (1) A schematic diagram of the roller shutter door operator in Example 1;

[0039] Figure 1 (2) Top view of the hand zipper and control circuit end cap of Embodiment 1;

[0040] Figure 2(1) A schematic diagram of the braking state of the braking device in Example 1;

[0041] Figure 2 (2) A schematic diagram of the brake device in the open state of Embodiment 1;

[0042] Figure 2 (3) Schematic diagram of the front cover of the brake device in Example 1;

[0043] Figure 3 This is an exploded view of the input axial cam and the output axial cam in Example 1;

[0044] Figure 4 (1) Front view of the transition wheel (spring groove omitted) in Embodiment 1;

[0045] Figure 4 (2) Schematic diagram of the interaction between the transition wheel (spring groove omitted) and the input axial cam (brake part omitted) in Embodiment 1;

[0046] Figure 5 This is a schematic diagram of the overall operation of the roller shutter door operator in Example 2;

[0047] Figure 6 (1) A schematic diagram of the braking state of the braking device in Example 2;

[0048] Figure 6 (2) This is a schematic diagram of the brake device in the open state in Example 2. Detailed Implementation

[0049] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0050] The following descriptions of the embodiments are made with reference to the accompanying drawings, illustrating specific embodiments in which the invention can be implemented. The directional and positional terms used in this invention, such as "upper," "middle," "lower," "front," "rear," "left," "right," "inner," "outer," and "side," are merely for reference to the accompanying drawings. Therefore, the directional and positional terms used are for illustrating and understanding the invention, and not for limiting the invention. Example 1

[0051] like Figure 1-3 The image shows a mechanical brake roller shutter door motor assembly, specifically, as follows: Figure 1As shown in (1), the roller shutter door machine includes a motor 1, a motor operation control circuit 6, a brake device 2, a gearbox 3, a hand-operated chain wheel 4, and a travel limiter 5; the output shaft of the gearbox 3 is fitted with a small sprocket, and the small sprocket drives a large sprocket fixed on the roller shutter door roller shaft through a chain, and the roller shutter door is wound around the roller.

[0052] like Figure 1 (2) As shown, the end cap of the hand chain wheel 4 is rotatably mounted on the roller shutter door motor assembly, so that the hand chain soft wheel can be rotated to adapt to the left or right installation requirements of the roller shutter door motor assembly. Specifically, the end cap 41 of the hand chain wheel and the end cap 61 of the control circuit 6 can be set separately. Of course, according to the appearance design requirements, the control circuit 6 can also be mounted in the assembly cavity of the travel limiter 5; the hand chain end cap is provided with the chain outlet 42 of the hand chain wheel 4.

[0053] like Figure 2 As shown in (1)-(3), the braking device 2 includes an anti-rotation part 21, an input axial cam 22, an output axial cam 23, and a reset mechanism. The output axial cam 23 is provided with a braking part 231. The input axial cam 22 is fixedly sleeved on the motor output shaft, and the output axial cam 23 is sleeved on a transition wheel 25. This is a schematic diagram of the braking state of the braking device in Embodiment 1. The transition wheel 25 is fixed on the input gear 31 of the gearbox 3. The transition wheel 25 and the input gear 31 are rotatably sleeved on the input shaft 32 of the gearbox 3 as a whole through a bearing. The inner side of the input axial cam 22 is rotatably fixed on the input shaft 32 through a bearing, and the outer side is fixed on the front end cover 28 of the braking device 2 through a bearing. The front end cover 28 of the braking device 2 is fixed at the lower end of the motor as the rear end cover of the motor. The elastic element 24 (compression spring) of the reset mechanism is located between the transition wheel 25 and the output axial cam 23.

[0054] A brake delay mechanism is provided between the anti-rotation part 21 and the brake part 231, so that after the input axial cam and the output axial cam disengage, braking only occurs when the brake part rotates 120° and acts on the anti-rotation part 211. Before this, or when the force exerted on the roller shutter door body by the transmission system is greater than or equal to the weight of the hanging part of the roller shutter door body, the output axial cam accelerates to rotate, causing the input axial cam and the output axial cam to rotate in opposite directions. During this process, accidental braking can be effectively avoided. Specifically, the anti-rotation part 21 includes three anti-rotation elements 211 and three anti-rotation grooves 212 that are evenly and alternately distributed circumferentially and fixed on the motor end cover 28; during braking (full braking), the relative rotation angle c between the input axial cam 22 and the output axial cam 23 is 0°, the braking part extends into the anti-rotation groove 212, and simultaneously acts on the three anti-rotation elements 211; when the input axial cam 22 and the output axial cam 23 rotate relative to each other, the output axial cam 23 undergoes axial movement, and the input axial cam 22 and the output axial cam 23 cannot completely disengage from the mutually inserted state, and the braking part extends into or disengages from the anti-rotation part.

[0055] In this embodiment, the input axial cam 22 can also be fitted onto the output shaft of the motor 1 with a limited rotation angle. For example, the motor output shaft has an external thread, and the input axial cam has a mounting hole for the motor output shaft. The mounting hole has an internal thread that matches the external thread. The input axial cam has an anti-disengagement groove for the motor output shaft, and the motor output shaft has a backstop ring at the end of the external thread. By designing the number of thread turns, such as 0.5, 0.8, 1, 2, etc., the maximum rotation angle of the input axial cam on the motor output shaft is constrained. When the relative rotation angle between the two reaches the maximum or minimum value, if they continue to rotate in the original rotation direction, they can rotate synchronously.

[0056] Similarly, in this embodiment, the transition wheel 25 can also be fitted onto the input gear 31 of the gearbox 3 with a limited rotation angle, and buffers are provided at the two ends of the rotation limit to achieve the technical goal of braking delay function.

[0057] like Figure 3 As shown, the input axial cam 22 has one or more input double-sloping protrusions 221 evenly distributed circumferentially on its wheel surface. In this embodiment, four protrusions are used (the number can also be adjusted according to the design requirements of the brake delay mechanism, such as three, five, or other numbers). The output axial cam 23 has four output double-sloping protrusions 232 evenly distributed circumferentially on its wheel surface. The input axial cam 22 and the output axial cam 23 are matched, and their rotation axes are on the same straight line. In the initial state (braking state), the apex of each output double-sloping protrusion of the output axial cam 23 abuts against the connection position M of two adjacent input double-sloping protrusions on the input axial cam 22. Specifically, the following should be satisfied:

[0058] The number of 360° anti-rotation components > the number of input or output double-sloping protrusions * transition angle (the transition angle is the relative rotation angle between the input axial cam and the output axial cam when the braking part moves from the lowest point to the highest point).

[0059] The reset mechanism is a set of compression springs mounted on the output axial cam 23. One end of the compression spring abuts against the end face of the brake part 231, and the other end abuts against the anti-disengagement groove of the transition wheel 25 (this scheme can also be replaced by: two or more compression springs circumferentially distributed on the output axial cam 23, each compression spring abutting against the end face of the brake part 231 at one end and against the anti-disengagement groove of the transition wheel 25 at the other end); the natural length of the compression spring is less than the axial length of the space that the compression spring can move when the brake part is farthest from the anti-rotation part.

[0060] The reset mechanism in this embodiment can also be: the braking part has elastic elements respectively arranged axially on the front and rear end faces.

[0061] The technical objective of the reset mechanism is to enable the brake part 231 to have a tendency to extend into the anti-rotation part when it is disengaged from the anti-rotation part; and / or to change the axial distance (axial position of the brake part) when the relative rotation angle between the input axial cam and the output axial cam changes.

[0062] The anti-rotation part and / or braking part are provided with a circumferential buffer part (torsion spring: allows the anti-rotation part and / or braking part to rotate or swing at a certain angle after interacting to prolong the braking time, which should be greater than the time required for the input axial cam and output axial cam to switch relative rotation directions in the initial stage of driving the roller shutter door downward, while buffering kinetic energy; damping plate).

[0063] In this embodiment, the input axial cam is located at the output shaft of a motor in the transmission system, and at the input shaft of a gearbox in the transmission system. The brake device 2 is located at the high-speed end of the transmission system. Since the brake device 2 of this invention uses circumferential contact instead of traditional friction braking and distributes the braking load through multiple anti-rotation components, it can also be located at the medium-speed end or the low-speed end.

[0064] like Figure 4As shown in (1)-(2), on the output axial cam 23, near the input axial cam 22, one component of the transition wheel 25 is provided with a counter-pressure protrusion E, and the other component is provided with inclined baffles F on both sides of the counter-pressure protrusion. Between the two inclined baffles F, a moving track G for the counter-pressure protrusion is provided along the axial direction. The inclined surface of the inclined baffle F faces the anti-rotation part 21, so that when the transition wheel 25 drives the output axial cam 23 to rotate relatively clockwise or relatively counterclockwise, the output axial cam 23 will be axially displaced in the direction closer to the anti-rotation part 21. (The counter-pressure protrusion E and the component with inclined baffles F are not fixed. The two components can be interchanged as needed. In this embodiment, the counter-pressure protrusion E is provided on the output axial cam 23, and the two inclined baffles F are provided on the transition wheel 25; or the counter-pressure protrusion E is provided on the transition wheel 25, and the two inclined baffles F are provided on the output axial cam 23.)

[0065] The connection between the inclined baffle F and the track G is located inside the anti-rotation part 21.

[0066] Working principle:

[0067] Both the input axial cam 22 and the output axial cam 23 have circumferentially distributed double-sloped protrusions on their abutting end faces to allow for axial displacement of the braking unit 231 in both forward and reverse rotation. However, they cannot immediately switch between forward and reverse rotation (the input axial cam 22 and the output axial cam 23 must rotate relative to each other by a certain angle to allow the other slope of the input axial cam 22 and the output axial cam 23 to abut again). When the input axial cam 22 and the output axial cam 23 are at their farthest distance from each other, the vertex of any double-sloped protrusion should be located within the set of points traversed by the double-sloped protrusion of the other axial cam in one revolution. Therefore, the angle at which they can rotate relative to each other is limited. That is, after a certain angle of relative rotation, the input axial cam 22 and the output axial cam 23 rotate synchronously, thus enabling the input axial cam 22 to drive the output axial cam 23 in one direction (braking occurs when the output axial cam is the sole power source for both).

[0068] Downward movement phase: When the motor starts, the input axial cam 22 acts on the positive inclined surface of the output axial cam 23, causing the brake part 231 to axially disengage from the anti-rotation part 21, restricting the source of motion of the gearbox 3 (door body). The movement switches from the anti-rotation part 21 to the motor shaft (using the anti-rotation part's limitation to keep the door body stationary; switching to: motor shaft / input gear restricting the door body's free fall). During the switching process, the gearbox drives the output axial cam to accelerate rotation, and the reverse inclined surface acts on the input axial cam / motor shaft. Before the positive inclined surface disengages and before the reverse inclined surface interacts, the brake part is only pressed against the anti-rotation part by the reset mechanism, resulting in forced braking. Traditional cam-mechanism brakes fail to consider this issue and cannot continue downward movement. This embodiment overcomes this problem by employing two mechanisms:

[0069] 1. Link the braking speed to the aforementioned switching speed.

[0070] 2. Ensure that the time required to complete braking is greater than the aforementioned state transition time.

[0071] Specifically as follows:

[0072] Since the axial displacement velocity of the reset mechanism is much higher than the axial velocity of the brake caused by the input / output axial cam action, the time it takes for the reset mechanism to push the brake into the anti-rotation section is negligible. The analysis begins at the point in time when the brake enters the anti-rotation section.

[0073] The motor shaft drives the input axial cam to rotate at a constant speed of v1; when the brake disengages from the anti-rotation device, the output axial cam and the input axial cam rotate synchronously at v1; then, the transition wheel / gearbox / roller shutter door body drives the output axial cam and brake to accelerate (the longer the door body extends, the greater the acceleration), and rotates at an accelerated speed of v2 (v2>>v1).

[0074] Time required to complete braking: t1 = (360° / n1) / v2 [t1 is very short, assuming a constant rotational speed v2]

[0075] The time required for switching between the forward and reverse inclined planes is: t2 = β / (v2-v1) ≈ β / v2, where the transition angle β is the rotation angle required for the braking unit to move from the lowest point A to the highest point B; n2 is the number of protrusions on the double inclined planes, and the rotation angle corresponding to each inclined plane is 360 / (2*n2); the inclined plane height is L1, the maximum stroke of the braking unit is L2, and β = 360 / (2*n2)*(L2 / L1).

[0076] t1>t2, therefore: 360° / (n1 / v2)>360 / (2*n2*v2)*(L2 / L1), therefore 1 / n1>(L2 / L1) / (2n2), therefore 2n2 / n1>L2 / L1

[0077] In this embodiment, the height L1 of the double-sloping protrusion (i.e., the maximum axial displacement that can occur) is 14cm, the depth of the anti-rotation part is 7mm, and the thickness of the braking part is 4mm; the maximum depth of the braking part extending into the anti-rotation part is 5mm, and the maximum distance from the anti-rotation part is 2cm. Therefore, the maximum stroke of the braking part is L2=5+2=7 (cm), and the length of the input axial cam and the output axial cam mating against each other is 14-7=7 (cm), which effectively ensures the stability of the motor-driven gearbox.

[0078] The fewer the number of protrusions n2 on the inclined plane, the smaller the slope of the inclined plane (the smaller the component force perpendicular to the inclined plane, and the smaller the friction), the smaller the resistance to the conversion of relative rotation into axial motion, and the longer the service life. At the same time, in order to ensure force balance, two protrusions on the inclined plane are the least resistant (the smaller the slope of the inclined plane, the longer the length of the inclined plane, and the longer the time t0 to complete the specified axial displacement will also be. In addition, as can be seen from the above formula, it is not necessarily better for n2 to be smaller.

[0079] The above problems can also be solved by:

[0080] Extend the reset time to complete the switching of the forward and reverse inclined planes before the braking part extends into the anti-rotation part; or make the reset stroke associated with the relative rotation stroke.

[0081] Upward movement: The input axial cam restricts the output axial cam from rotating in the opposite direction (door falls), and then switches to the input axial cam to resist the reverse rotation of the output axial cam with minimal resistance. That is, the interaction force between the input axial cam and the output axial cam is extremely strong. The output axial cam is extended into the anti-rotation part by the reset device and brakes after rotating a certain angle.

[0082] Downward movement: The input axial cam restricts the rapid rotation of the output axial cam (the door falls off due to electric shock), and then switches to the input axial cam to resist the high-speed rotation of the output axial cam with minimal resistance. That is, the interaction force between the input axial cam and the output axial cam is extremely strong. The output axial cam is extended into the anti-rotation part by the reset device and brakes after rotating a certain angle.

[0083] The reason why the door and gearbox remain stationary when the power is off is that the friction between the brake disc and the break-in bracket overcomes the weight of the door, thus preventing the door from falling. The reason why the door does not fall freely when the power is on is that the door is pulled by the motor shaft through the gearbox. The accurate reason why the brake disc rotates forward and backward relative to the motor when the door is moving downward is that the force on the brake disc changes instantaneously, causing the motor shaft to actively act on the brake disc, and then passively act on the brake disc.

[0084] In this embodiment, the reset member, especially when using only scheme IV, i.e., only through the cooperation of the counter-pressure protrusion and the inclined baffles on both sides, should satisfy: tan(y)≥tan(x) or y≥x. Furthermore, the number of double inclined protrusions of the clutch input member is less than the number of counter-pressure protrusions. It should be noted that this formula is not limited to the reset member, especially when only scheme IV is used. Example 2

[0085] like Figure 5 , 6 As shown in Embodiment 1, the mechanical brake roller shutter door assembly can also employ the following braking device:

[0086] One of the input axial cam 22' and the output axial cam 23' is provided with a positive and negative threaded groove or a threaded hole, and the other component is provided with a synchronizing protrusion, so that when the relative rotation angle of the input axial cam 22' and the output axial cam 23' changes, the mutual axial distance (axial position of the braking part) changes. Specifically, in this embodiment, the input axial cam is provided with a positive and negative threaded groove, the output axial cam is provided with a synchronizing protrusion, the output axial cam is fitted inside the input axial cam, and the synchronizing protrusion extends into the positive and negative threaded groove; the output axial cam 23' is provided with a braking part 231'. Alternatively, as needed, the output axial cam 23' can be provided with a positive and negative threaded groove, the input axial cam is provided with a synchronizing protrusion, the input axial cam 22' is fitted inside the output axial cam 23', and the synchronizing protrusion extends into the positive and negative threaded groove.

[0087] The input axial cam 22' is fixedly fitted with a baffle 26' with a spring 24', and the output axial cam 23' is axially displaceable and fitted onto a transition wheel 25', which is fixed to the input shaft of the gearbox.

[0088] Assembly sequence:

[0089] (1) The input axial cam 22' extends into the output axial cam 23', so that the positive and negative threaded grooves and the synchronous protrusions abut against each other;

[0090] (2) Spring 24', baffle 26' and retaining ring (anti-reverse ring) of baffle 26' are sequentially sleeved on the input axis cam 22';

[0091] (3) Insert the input axial cam 22' into the bearing on the end cover of the brake device, and set a retaining ring (anti-reverse ring) at position 27'.

[0092] like Figure 5-6 As shown, the main components involved in this embodiment include: motor 1', brake device 2', gearbox 3', hand chain wheel 4', travel limiter 5', anti-rotation part 21' and anti-rotation component 211'.

[0093] Working principle:

[0094] The assessment criteria for determining whether accidental braking will occur include at least the total rotation angle d caused by the axial reciprocating displacement of the output axial cam 23' after it disengages from the anti-rotation element 211'. Specifically, during the downward movement: in the initial stage of motor startup, the positive thread groove of the input axial cam 22' acts on the synchronous protrusion of the output axial cam 23', causing the braking part 231' to move axially towards the input axial cam 22' along with the output axial cam 23', until the input axial cam and the output axial cam rotate relative to each other (c). maxThe angle is adjusted, and the anti-rotation part is disengaged. The synchronous protrusion moves along the positive thread groove to the middle of the positive thread groove, and the input axial cam and the output axial cam rotate synchronously. V in =V ou t; then the output axial cam rotates faster due to the falling of the roller shutter door (V in <V out This causes the synchronizing protrusion to act in the opposite direction on the positive thread groove of the input axial cam, until the synchronizing protrusion moves to the connection position of the positive and negative thread grooves, thereby causing the input axial cam and the output axial cam to rotate in opposite directions relative to each other. max Subsequently, the braking unit moves in the opposite axial direction to the output axial cam and extends into the anti-rotation part (because it needs to continue rotating 120° - the relative rotation angle c between the input axial cam and the output axial cam). max (After it touches the anti-rotation component), because 2c max The angle is less than 120°, therefore no braking occurred at that point in time; immediately afterwards, the synchronizing protrusion acts on the reverse threaded groove, causing the output axial cam to axially displace away from the input axial cam, until the relative rotation angle between the input and output axial cams is -c. max The braking unit disengages from the anti-rotation unit, and the input axial cam and output axial cam begin to rotate synchronously. Due to 2c max The angle is less than 120°, so there will be no accidental braking during the entire process.

[0095] Comparing Examples 1 and 2, it can be found that:

[0096] The working principle of Example 1 is more likely to be: after the braking part of the output axial cam disengages from the anti-rotation component, it does not need to make axial displacement during the switching of forward and reverse rotation with the input axial cam; in order to reduce the possibility of accidental braking, the braking component should be prevented from extending into the anti-rotation groove during this process.

[0097] The working principle of Example 2 is more likely to be: after the brake part of the output axial cam disengages from the anti-rotation component, it will inevitably make axial displacement synchronously with the input axial cam during the switching of forward and reverse relative rotation. That is, the brake part will inevitably extend into the anti-rotation component during this process. In order to avoid axial interference between the brake part and the anti-rotation component, it is necessary to ensure that the brake part can extend into the anti-rotation groove when it moves in the opposite axial direction.

[0098] Therefore, we can conclude that:

[0099] The clutch input and clutch output are fitted with matching double-sloping protrusions. The trajectory of the brake part on the end face of the anti-rotation part should be as large as possible. The anti-rotation groove should be such that the brake part just falls into it. The anti-rotation groove is provided with an inlet. Specifically, the anti-rotation groove and the brake part are fitted with a clearance. In one cycle, the cumulative rotation angle of the brake part through all the anti-rotation ends and anti-rotation grooves is equal to 360°.

[0100] The clutch input and clutch output components are fitted with matching positive and negative screw holes or grooves and synchronous protrusions. The trajectory on the anti-rotation end face of the braking part should be as small as possible, while the trajectory in the anti-rotation groove should be as large as possible. Example 3

[0101] like Figure 3 As shown in Embodiment 1, the braking device of the mechanical brake roller shutter door assembly is replaced with the following:

[0102] The braking device includes an anti-rotation part and one or more sets of limited-rotation components. Each set of limited-rotation components includes an input radial cam and an output radial cam. At least one of the output radial cam and the input radial cam is provided with or drivenly connected to a braking part. The input radial cam is drivenly connected to the output radial cam. The maximum relative rotation angle c between the input radial cam and the output radial cam is... max The absolute value of the input radial cam is greater than 0 and less than infinity. At least one of the input radial cam and the output radial cam is provided with a reset mechanism, so that when the input radial cam and the output radial cam rotate relative to each other, the braking part and the anti-rotation part have a state change of contact and discontinuation. When the absolute value of the relative rotation angle c between the input radial cam and the output radial cam is greater than 0, the braking part and the anti-rotation part have a tendency to move closer to each other. A brake delay mechanism is provided between the anti-rotation part and the braking part, so that when the reset mechanism returns to the initial state, the anti-rotation part and / or the braking part need to rotate a non-0° angle before interacting with each other. The force exerted by the anti-rotation part on the roller shutter door body through the transmission system is greater than or equal to the weight of the hanging part of the roller shutter door body.

[0103] Working principle:

[0104] The downward movement of the roller shutter door is divided into 3 stages.

[0105] Initial state (braking state): The anti-rotation part restricts the rotation of the braking part (along with the clutch output component), and the clutch output component restricts the rotation of the transition wheel (gearbox and roller shutter load).

[0106] After the motor is powered on, the motor output shaft drives the clutch input component to act on the clutch output component. The clutch output component, under the action of the anti-rotation part, overcomes the force of the reset mechanism and moves axially, disengaging from the anti-rotation part. At the instant: circumferentially, because the circumferential component of the "clutch input component", the "circumferential component of the reset mechanism", and the "transition wheel" rotate in the same direction, the clutch output component is accelerated by the combined action of the "reset mechanism", the "transition wheel", and the "clutch input component". The initial speed of the clutch output component is 0, and the initial speed of the transition wheel is 0. Axially, the "clutch output component", under the combined action of the "reset mechanism" and the "clutch input component", moves towards the anti-rotation part with an initial velocity of 0.

[0107] At the instant of rotation, the "clutch output component" is simultaneously acted upon by three components: the "reset mechanism," the "clutch input component," and the "gearbox." Meanwhile, the "transition wheel," moving in the same direction, is acted upon only by the "gearbox." Therefore, the acceleration 'a' of the "clutch output component" at that instant is... out Larger than "transition wheel" a g The angular velocity quickly exceeds that of the "transition wheel." Due to the limitation of the moving track G, the "clutch output component" quickly reverses and drives the "transition wheel" to accelerate. The speeds of both increase synchronously, but a out Much smaller than the acceleration a of the transition wheel g As the axial displacement of the clutch output component reaches its limit, the clutch output component and the clutch input component instantly achieve synchronous rotation. Immediately afterwards, because the reset mechanism and the clutch input component exert opposite forces on the clutch output component in the axial direction, they maintain their influence on the clutch output component throughout this acceleration process, thus maintaining the angular velocity v of the clutch output component. out Angular velocity v greater than the "clutch input" in When the angular velocity v of the "transition wheel" g Greater than "clutch output" v out Similarly, due to the limitation of the moving track G, the "transition wheel" once again drives the "clutch output component" to continue to accelerate synchronously, the angular velocity difference between the clutch output component and the clutch input component is further increased, and the clutch output component abuts against the other inclined surface of the "clutch input component" before falling into the anti-rotation groove.

Claims

1. A mechanically braked roller shutter door motor assembly, the roller shutter door motor comprising a motor, a motor operation control circuit, a braking device, and a gearbox, wherein the output shaft of the motor drives and is connected to the gearbox, the output component of the gearbox drives and is connected to the roller of the roller shutter door, and the braking device is connected to the transmission system consisting of the motor output shaft and the roller input component; characterized in that: The braking device includes an anti-rotation part and one or more sets of limited-rotation components. Each limited-rotation component set includes a clutch input and a clutch output. At least one of the clutch output and clutch input is provided with or tractively connected to a braking part. The clutch input is tractively connected to the clutch output. The maximum relative rotation angle c between the clutch input and clutch output is... max The absolute value of the clutch input component is greater than 0 and less than infinity. At least one of the clutch input component and the clutch output component is provided with a reset mechanism, so that when the relative rotation angle c between the clutch input component and the clutch output component is not 0, the clutch input component and the clutch output component have a rotation tendency to restore the rotation angle c to 0. The braking device is also provided with a braking delay mechanism, so that after the clutch input component and the clutch output component rotate in opposite directions, there is at least a time period t greater than 0. The braking delay mechanism acts on the reset mechanism, the clutch output component, or the clutch input component, and satisfies that during the process of the clutch output component and the clutch input component rotating in opposite directions, the braking part and the anti-rotation part will not brake due to interaction.

2. The mechanical brake roller shutter door motor assembly as described in claim 1, characterized in that: The clutch input component is an input axial cam, and the clutch output component is an output axial cam. The input axial cam and the output axial cam abut against each other. When the input axial cam and the output axial cam rotate relative to each other, at least one of the input axial cam and the output axial cam undergoes axial movement, causing the braking part to extend into or disengage from the anti-rotation part. The input axial cam is fixedly or rotatably mounted on the transmission component above the input axial cam in the transmission system, and the output axial cam is axially movable and mounted on the transmission component below the output axial cam in the transmission system.

3. A mechanical brake roller shutter door motor assembly as described in claim 1 or 2, characterized in that: The reset mechanism includes one or more elastic elements, and has the following characteristics: the natural length of the elastic element is less than the axial length of the space in which the elastic element can move when the braking part is furthest from the anti-rotation part, and / or the braking part has the elastic elements respectively arranged axially on the front and rear end faces.

4. The mechanical brake roller shutter door motor assembly as described in claim 1, characterized in that: The brake delay mechanism has one or more brake delay spaces along the direction of the interaction force between the anti-rotation part and the braking part on the movement path to achieve braking. and / or The braking delay mechanism satisfies the following condition: the rotation time T of the clutch input and clutch output components from the relative rotation limit state in one direction to the relative rotation limit state in the other direction is less than t.

5. The mechanical brake roller shutter door motor assembly as described in claim 1, characterized in that: The next stage of the transmission component in the transmission system is a transition wheel; the reset mechanism has a counter-pressure protrusion on one component and inclined baffles on both sides of the counter-pressure protrusion on the other component at a position close to the clutch output component and the transition wheel; the inclined baffles face the anti-rotation part, so that when the transition wheel drives the clutch output component to rotate relatively clockwise or relatively counterclockwise, the clutch output component will be displaced in the direction closer to the anti-rotation part.

6. The mechanical brake roller shutter door motor assembly as described in claim 5, characterized in that: The contact area between the clutch input and clutch output components includes one or more circumferentially distributed double-sloping protrusions.

7. The mechanical brake roller shutter door motor assembly as described in claim 6, characterized in that: The number of double-beveled protrusions in the clutch input component is less than the number of counter-pressure protrusions.

8. The mechanical brake roller shutter door motor assembly as described in claim 5, characterized in that: The anti-rotation part includes two or more anti-rotation components, which are fixed on the motor end cover; when braking, the braking part acts on at least two anti-rotation components simultaneously.

9. The mechanical brake roller shutter door motor assembly as described in claim 8, characterized in that: The anti-rotation component and the double-sloped protrusion should satisfy the following: 360° / number of anti-rotation components n1 > number of double-sloped protrusions n2 * transition angle β; the transition angle β is the relative rotation angle between the clutch input component and the clutch output component when the braking part moves from the lowest point to the highest point. and / or The anti-rotation component and the double-sloped protrusion should satisfy: 2n2 / n1 > L2 / L1; where n1 is the number of anti-rotation components, n2 is the number of double-sloped protrusions, and L1 is the slope height of the double-sloped protrusion. ， L2 is the maximum stroke of the L-type brake unit.

10. The mechanical brake roller shutter door motor assembly as described in claim 5, characterized in that: Let x be the angle between the inclined surface of the inclined baffle and the axial direction, and y be the angle between the contact surfaces of the clutch input and clutch output components and the axial direction. Then we have tan(y)≥tan(x) or y≥x.

11. A mechanical brake roller shutter door motor assembly as described in claim 1, 2, 5, or 6, characterized in that: The anti-rotation part includes one or more anti-rotation elements and one or more anti-rotation grooves; the cumulative rotation angle of the braking part after passing through all anti-rotation elements and anti-rotation grooves is equal to 360°.

12. A mechanical brake roller shutter door motor assembly as described in claim 1, 2, 5, or 6, characterized in that: When the braking unit is disengaged from the anti-rotation unit, the force exerted by the reset mechanism on the component with the reset mechanism in the clutch input and clutch output components is less than the force exerted by the clutch input on the clutch output.

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