WO2012089130A1

WO2012089130A1 - Fall-proof, overspeed-proof space and wedge emergency braking apparatus for use in lift

Info

Publication number: WO2012089130A1
Application number: PCT/CN2011/084842
Authority: WO
Inventors: 洪涛
Original assignee: Hong Tao
Priority date: 2010-12-30
Filing date: 2011-12-28
Publication date: 2012-07-05
Also published as: CN102556798A; CN102556798B

Abstract

A fall-proof and overspeed-proof space and wedge emergency braking apparatus for use in a lift. The apparatus comprises a wedge control mechanism and a rotatable space and wedge braking mechanism. The wedge control mechanism comprises an actuating mechanism and a triggering mechanism (AC). The space and wedge braking mechanism is a sealed, axial-force self-activated friction coupling mechanism having a high torque capacity, comprising a rotational guiding mechanism (G) consisting of a guiding member (50) having a spiral guiding face arranged thereon and an intermediary member (90), and surface contact rotary friction mechanisms (F1, and F2) constituted by a frictional member (70) and the guiding member (50) and the intermediary member (90) respectively. The wedge control mechanism comprises the purely mechanical centrifugal triggering mechanism (AC) and a circumferential limiting mechanism, for use in controlling the engagement of the braking mechanism. In addition to responding to centrifugal motion, the triggering mechanism (AC) at the same time is capable of responding to a cable-rupture or chain-rupture signal, an electronic overspeed signal, and signals for power-outage due to malfunction and normal power-outage/shutdown. The emergency braking apparatus is universally applicable to all lifts, and is highly reliable and safe, structurally simple, structurally compact, and inexpensive.

Description

升降设备用空间楔合式防坠落、防超速紧急制动装置相关申请 Space-wedge type fall prevention and overspeed emergency brake device for lifting equipment

本申请是本申请人提出的名为空间楔合式摩擦超越离合器的中国专利申请 This application is a Chinese patent application filed by the applicant named Space Wedge Friction Overrunning Clutch.

201010222712.X和 201020186785.3的从属专利申请。该公开在先的两项专利申请的全部内容通过引用结合于此。技术领域 A dependent patent application of 201010222712.X and 201020186785.3. The entire contents of the two prior patent applications are hereby incorporated by reference. Technical field

本发明涉及卷扬、提升、牵引设备以及热动力领域中的一种制动装置，以及包括该装置的离合装置，特别涉及一种防止被制动物体坠落和 /或超速运动的紧急制动装置。背景技术 The present invention relates to a brake device in the field of hoisting, lifting, traction and thermal power, and a clutch device including the same, and more particularly to an emergency brake device for preventing falling and/or overspeed movement of a braked object . Background technique

依据现有技术的电梯，无论是借助钢绳曳引机驱动的轿厢 /罐笼式，借助链条驱动的自动扶梯式，还是借助齿轮齿条驱动的施工吊笼式，它们各自防坠落和 /或防超速的紧急制动器 /***都存在着某些不足，且互不通用。例如一，应用于轿厢式电梯的安全钳装置，其楔合式制动方式，必需全高程的导轨侧面具有足够的平面精度且不被污染。仅这一基本要求，就直接决定了该类电梯难以使用于开放的户外等空间，缩小了应用领域的同时，更增大了制作和维护的成本。而即便使用于密闭的井道，其制动摩擦面仍是长期暴露在外的，只是受污染的程度降低了一些，并未得到实质的改善，再加上装置构件过多，因此不具有足够的可靠性。另外，该装置必需辅以包括限速绳等的复杂的限速器***，不仅增加了电梯的成本和所占用的空间，而且更直接降低了其可靠性和安全性。文献 CN101107189A和 CN1594057A便详细指出了其中的缺点和不足。 Elevators according to the prior art, whether by car/cage driven by a steel wire traction machine, by escalator type driven by a chain, or by construction cages driven by rack and pinion, each of which is protected against falling and/or There are certain deficiencies in the anti-overspeed emergency brakes/systems that are not common to each other. For example, the safety clamp device applied to the car elevator has a wedge-type braking method, and the side of the full elevation rail must have sufficient plane precision and is not polluted. Only this basic requirement directly determines that such elevators are difficult to use in open outdoor spaces, which reduces the application area and increases the cost of production and maintenance. Even if it is used in a closed hoistway, its brake friction surface is still exposed for a long time, but the degree of pollution is reduced, and it has not been substantially improved. In addition, the device components are too much, so it is not reliable enough. Sex. In addition, the device must be supplemented by a complicated speed limiter system including a speed limit rope, etc., which not only increases the cost and space occupied by the elevator, but also directly reduces its reliability and safety. The disadvantages and disadvantages are pointed out in detail by CN101107189A and CN1594057A.

例如二，应用于自动扶梯 Z移动人行道的紧急制动装置，其中的棘轮式等有级制动伴随有显著的冲击甚至是刚性冲击，常破坏驱动主轴与梯级的配合精度而必需事后调整；其中的摩擦式制动则电耗过大，断电便不能正常工作。而且转矩容量相对较小，结构较复杂。 For example, the emergency braking device applied to the escalator Z moving walkway, wherein the ratchet-type stepped brake is accompanied by a significant impact or even a rigid impact, often destroying the matching precision of the driving spindle and the step, and must be adjusted afterwards; The friction brake has excessive power consumption and cannot be operated normally due to power failure. Moreover, the torque capacity is relatively small and the structure is complicated.

例如三，应用于齿轮齿条式施工电梯的紧急制动装置 /防坠安全器，虽然其所有制动摩擦面均处于最佳的密封状态，但由于属于有源制动（如弹簧力），与现有技术中所有摩擦式制动器一样，因其转矩容量仅仅取决于并敏感于其所得到的接合能量以及相关摩擦系数，而必需为匹配该接合能量与制动转矩耗费更多的资源和经济成本。作为结果，却没有得到足够的制动容量以及足够的制动可靠性。另外，该类施工电梯更因其制动方式而使整个驱动***成为其永久的载荷，以及因全程齿轮式驱动方式，而具有电耗大、噪声高、震动大、运行平稳度差等缺点。 For example, the emergency brake/anti-fall safety device applied to the rack-and-pinion type construction elevator, although all the brake friction surfaces are in an optimal sealing state, but because it is an active brake (such as spring force), Like all friction brakes in the technology, because the torque capacity only depends on and is sensitive to the joint energy and the relevant friction coefficient, it is necessary to spend more resources and economy to match the joint energy and braking torque. cost. As a result, there is not enough braking capacity and sufficient braking reliability. In addition, this type of construction elevator makes the whole drive system its permanent load due to its braking mode, and has the disadvantages of high power consumption, high noise, large vibration, and poor running stability due to the full-gear drive mode.

另外，在诸如斜坡车厢，登山铁路，提升车辆的机械装置，缆车轨道*** 等的整个卷扬、提升和牵引设备领域中，依据现有技术的紧急制动装置均存在类似的问题。发明内容 In addition, similar problems exist in prior art emergency braking devices in the field of overall hoisting, lifting and traction equipment such as ramp cars, mountain railways, mechanical mechanisms for lifting vehicles, cable car track systems and the like. Summary of the invention

本发明致力于设计基于全新技术原理的制动装置，以避免上述缺点。 The present invention is directed to designing a brake device based on a completely new technical principle to avoid the above disadvantages.

本发明要解决的技术问题是提供一种升降设备用空间楔合式防坠落、防超速紧急制动装置，其具有适用于开放式空间，适用于钢绳曳引式电梯、齿轮齿条驱动式施工电梯以及链条驱动式自动扶梯 /移动人行道，操纵简便且易于线控，工作可靠性更高，结构更简单更紧凑，占用空间更小，成本更低的优点。 The technical problem to be solved by the present invention is to provide a space wedge-type fall arresting and anti-overspeed emergency braking device for lifting equipment, which is suitable for an open space, and is suitable for steel rope traction type elevator and rack and pinion driven construction. Elevators and chain-driven escalators/moving walkways are easy to operate and easy to wire, have higher operational reliability, simpler and more compact structure, smaller footprint and lower cost.

为解决上述技术问题，本发明之升降设备用空间楔合式防坠落、防超速紧急制动装置包括，绕一轴线回转且可轴向接合的至少一个牵引摩擦机构，其具有绕所述轴线回转并均设置有摩擦面的至少大致为环状的中介件和摩擦件，以在该两构件间传递摩擦转矩；为该牵引摩擦机构提供接合力并绕上述轴线回转的至少一个转动导向机构，其具有绕上述轴线回转并均设置有相应导向面的至少大致为环状的导向件和中介件；以及，至少间接地设置在导向件、中介件或摩擦件上的操动机构和触发机构，前者用以至少间接地控制中介件的入楔动作，后者用以响应于输入信号而促动操动机构，以至少间接地致使中介件入楔，从而致动紧急制动装置；当导向件和摩擦件被中介件可驱动地连接成一个摩擦体时，导向件与中介件双方的导向面之间的相互抵触部位的升角 λ，大于零且小于等于 ξ , 即， 0 < λ ξ，其中， ξ是能够令形成于该抵触部位的导向摩擦副自锁的升角 λ的最大值。 In order to solve the above technical problem, the space wedge type fall prevention and overspeed emergency braking device for a lifting device of the present invention includes at least one traction friction mechanism that is swung around an axis and axially engageable, and has a rotation about the axis and An at least substantially annular intermediate member and a friction member each having a friction surface for transmitting frictional torque between the two members; at least one rotary guiding mechanism for providing an engagement force to the traction friction mechanism and rotating about the axis, An at least substantially annular guide member and an intermediate member that are disposed about the axis and are each provided with a corresponding guide surface; and an operating mechanism and a trigger mechanism that are at least indirectly disposed on the guide member, the intermediate member or the friction member, the former a wedge action for controlling the interposer at least indirectly, the latter for actuating the operating mechanism in response to the input signal to at least indirectly cause the interposer to wedge into the wedge, thereby actuating the emergency braking device; When the friction member is drivingly coupled to form a friction body by the intermediate member, the mutual guiding between the guiding member and the guiding surface of the intermediate member Lead angle [lambda] of the scanning points, greater than zero and less than or equal to [xi], i.e., 0 <λ ξ, where, [lambda] [xi] is the maximum value of the lead angle can be so formed in the abutment position of the self-locking friction guide.

为最佳地封闭轴向力，可设置有两个绕上述轴线回转的可轴向接合的摩擦机构，其中一个是上述牵引摩擦机构，其中另一个是与导向件和摩擦件至少不可旋转地分别结合在一起的传力摩擦机构，或者再一个上述牵引摩擦机构。 In order to optimally close the axial force, two axially engageable friction mechanisms can be provided which are pivoted about the above-mentioned axis, one of which is the traction friction mechanism described above, and the other of which is at least non-rotatably different from the guide member and the friction member. A combined force transmitting friction mechanism, or another traction traction mechanism as described above.

可选地，上述升角 λ的取值范围还可以是： ζ < λ ξ , 或者， 0 < λ ζ (当 ζ > 0 ), 其中， ζ是能够令所述抵触部位的导向摩擦副自锁的升角 λ的最小值，也是令牵引摩擦机构的牵引摩擦副自锁的升角 λ的最大值。 Optionally, the range of the rising angle λ may further be: ζ < λ ξ , or 0 < λ ζ (when ζ > 0 ), wherein ζ is capable of self-locking the guiding friction pair of the abutting portion The minimum value of the lift angle λ is also the maximum value of the lift angle λ of the traction friction pair of the traction friction mechanism.

较佳地，还可包括有至少一个限力元件，其可与导向件、中介件和摩擦件中的至多一个，以至少不可旋转的方式连接成力封闭式组合构件，以建立相互之间的轴向力封闭式抵触连接。 Preferably, the method further includes at least one force limiting member connectable to at least one of the guide member, the intermediate member and the friction member in at least one non-rotatable manner to form a force-closed composite member to establish mutual The axial force is closed against the connection.

优选地，上述导向件、中介件、摩擦件或限力元件是袋形构件，用以建立相互之间的轴向力封闭式抵触连接，其设置有绕上述轴线回转的至少大致半周的内周面，以及位于该内周面上的大致半周的周向凹槽和由上述袋形构件的外周面连通至该周向凹槽的入口。 Preferably, the guiding member, the intermediate member, the friction member or the force limiting member is a pocket member for establishing an axial force closed contact connection with each other, and is provided with an inner circumference of at least substantially a half revolution around the axis a face, and a substantially half-circumferential circumferential groove on the inner peripheral surface and an inlet connected to the circumferential groove by the outer peripheral surface of the bag-shaped member.

可选地，还包括至少一个弹性元件，其设置在位于转动导向机构的至少一个轴向端的两个轴向 4氏触面之间，以形成弹性的轴向封闭力。 Optionally, at least one resilient member is further disposed between the two axially-shaped contact faces at the at least one axial end of the rotary guide mechanism to form an elastic axial sealing force.

优选地，导向件和中介件的导向面是螺旋型齿面，其设置在该二构件的包括端面、内周面和外周面的一个表面上；在轴平面内，该螺旋型齿面与上述轴线之间的夹角大于 0度，小于 180度。 Preferably, the guiding surface of the guiding member and the intermediate member is a spiral tooth surface disposed on a surface of the two members including the end surface, the inner circumferential surface and the outer circumferential surface; in the axial plane, the spiral tooth surface and the above The angle between the axes is greater than 0 degrees and less than 180 degrees.

可选地，还包括至少具有一个弹性元件的弹性预紧机构，其用于持续地保持中介件与摩擦件之间的至少间接的摩擦连接。 Optionally, an elastic pretensioning mechanism having at least one resilient member is also included for continuously maintaining at least an indirect frictional connection between the intermediate member and the friction member.

可选地，限力元件是具有中心圓孔的杯形壳。较佳地，限力元件可包括径向上至少大致对称的两个半圓壳和至少一个环形箍，该两个半圓壳的形状具有这样的组合效果，即，二者径向对接所构成的组合构件，设置有绕上述轴线的中心圓孔以及位于该中心圓孔内周面上的绕所述轴线的周向凹槽；上述环形箍以设置在组合构件的中部或外端部的外周面上的形式，固定住该组合构件。 Optionally, the force limiting element is a cup-shaped shell having a central circular aperture. Preferably, the force limiting element may comprise two semi-circular shells and at least one annular hoop at least substantially symmetric in the radial direction, the shape of the two semi-circular shells having such a combined effect, that is, the combined members formed by the radial joints of the two a central circular hole around the axis and a circumferential groove around the axis on the inner circumferential surface of the central circular hole; the annular hoop being disposed on the outer circumferential surface of the central portion or the outer end portion of the composite member, The composite member is fixed.

可选地，牵引摩擦机构和传力摩擦机构中的至少一个，其两个相应摩擦面是半锥顶角大于 0度而小于 180度的截锥面。 Optionally, at least one of the traction friction mechanism and the force-transmitting friction mechanism, the two corresponding friction surfaces are truncated cone surfaces having a half cone angle apex greater than 0 degrees and less than 180 degrees.

为增大 ζ和 ξ，牵引摩擦机构可以是多摩擦片式摩擦机构，其具有与摩擦件和中介件分别不可旋转相连的两组轴向交错排列的各至少一个摩擦片。 To increase the ζ and ξ, the traction friction mechanism may be a multi-friction disc friction mechanism having two sets of axially staggered at least one friction lining that are non-rotatably coupled to the friction member and the intermediate member, respectively.

为增大转矩容量，传力摩擦机构可以是多摩擦片式摩擦机构，其具有与摩擦件和导向件分别不可旋转相连的两组轴向交错排列的各至少一个摩擦片。 To increase the torque capacity, the force-transmitting friction mechanism may be a multi-friction disc friction mechanism having two sets of axially staggered at least one friction plates that are non-rotatably coupled to the friction member and the guide member, respectively.

优选地，触发机构包括有离心装置，其具有离心配重，限力弹簧和绕上述轴线且至少间接地设置在转动件上的随动座环，以响应于该转动件超过设定转速时的离心力而动作。该转动件是导向件、中介件或摩擦件。 Preferably, the triggering mechanism comprises a centrifugal device having a centrifugal weight, a force limiting spring and a follower ring disposed around the axis and at least indirectly on the rotating member in response to the rotating member exceeding a set rotational speed Operate with centrifugal force. The rotating member is a guide member, an intermediate member or a friction member.

可选地，操动机构可包括周向自由度大于等于零的周向限位机构，该限位机构具有至少一个限位凸起，以及可对应地收纳该凸起的限位凹槽，两者至少间接地分别设置在中介件和导向件上；当限位凸起收纳至限位凹槽时，中介件在两个圓周方向上均不能自由地入楔。最佳地，该限位凸起至少具有周向弹性，周向限位机构的周向自由度等于零。 Optionally, the operating mechanism may include a circumferential limiting mechanism with a circumferential degree of freedom greater than or equal to zero, the limiting mechanism having at least one limiting protrusion, and a limiting groove correspondingly accommodating the protrusion, both At least indirectly disposed on the intermediate member and the guiding member; when the limiting projection is received into the limiting recess, the intermediate member is not freely wedged in both circumferential directions. Preferably, the limiting projection has at least circumferential elasticity, and the circumferential freedom of the circumferential limiting mechanism is equal to zero.

可选地，输入信号至少包括机械信号和电信号之一，并至少响应于驱动用钢丝绳断开，驱动用链条断开，升降设备的运行方向和速度不符合设定值，非正常断电，正常停电以及正常停机中的一种情形而产生。 Optionally, the input signal includes at least one of a mechanical signal and an electrical signal, and at least the driving wire is disconnected, the driving chain is disconnected, the running direction and speed of the lifting device do not meet the set value, and the power is abnormally powered off. A situation occurs during normal power outages and normal outages.

作为一种改进，紧急制动装置还包括受触发机构控制的闩锁机构，其至少间接地设置在导向件、中介件或摩擦件上，以在闭锁工况中，持续地约束住操动机构，进而维持住中介件的解楔状态，而在受到触发机构促动后的解锁工况中，则持续地解除其对操动机构的所述约束，以至少间接地致使中介件入楔。 As an improvement, the emergency brake device further includes a latch mechanism controlled by the trigger mechanism, which is at least indirectly disposed on the guide member, the intermediate member or the friction member to continuously restrain the operating mechanism in the latching condition And maintaining the unwrapped state of the interposer, and in the unlocking condition after being actuated by the triggering mechanism, the constraint on the operating mechanism is continuously released to at least indirectly cause the interposer to enter the wedge.

一种再改进是，操动机构还可包括绕上述轴线设置的无级支撑机构，其设置在限力元件和被支撑件之间，以轴向无级地移动该被支撑件的方式，建立限力元件与导向件、中介件以及摩擦件之间的轴向力封闭式抵触连接。该被支撑件是导向件、中介件和摩擦件中与限力元件不可旋转相连的那一个。 In a further improvement, the operating mechanism may further include a stepless support mechanism disposed around the axis, which is disposed between the force limiting member and the supported member, and moves the supported member in an axially stepless manner to establish The axial force-closed contact connection between the force-limiting element and the guide member, the intermediate member and the friction member. The supported member is the one of the guide member, the intermediate member and the friction member that is non-rotatably connected to the force limiting member.

进一步地，该无级支撑机构包括绕所述轴线设置且至少呈大致环状的支撑件，其通过轴向抵触和转动导向两种连接方式，分别连接至限力元件和被支撑件，其外周面上设置有部分轮齿。无级支撑机构还包括作用至支撑件的蓄能弹簧，其用于将支撑件持续地弹压向可以致使无级支撑机构建立上述轴向力封闭式抵触连接的方向。而且，该支撑件相对限力元件的周向自由度，至少大到致使无级支撑机构可以建立上述轴向力封闭式抵触连接的程度。 Further, the stepless support mechanism includes a support member disposed around the axis and at least substantially annular, which is connected to the force limiting member and the supported member by the axial connection and the rotation guide, respectively, and the outer periphery thereof Some teeth are provided on the surface. The stepless support mechanism also includes an energy storage spring that acts on the support member for continuously biasing the support member in a direction that causes the stepless support mechanism to establish the axial force closed contact connection. Moreover, the circumferential freedom of the support member relative to the force limiting member is at least as large as to enable the stepless support mechanism to establish the extent of the axial force closed contact connection described above.

更进一步地，其円锁机构具有可转动地设置在限力元件上的行星组合轮，其位于限力元件内部的部分，固定有啮合至支撑件的部分轮齿的行星齿轮，其位于限力元件外部的部分，固定有锁止件；还具有可转动地设置在限力元件上的触发件，被触发机构触发之前，该触发件可维持与锁止件的卡合，以持续阻止锁止件的自转，而被触发机构触发之后，该触发件将解除其与锁止件的卡合。另一种再改进是，操动机构包括摩擦式止转机构，其具有不可旋转地和至少间接地设置在摩擦件上的至少一个止转件，用以受控地摩擦抵触至中介件，以及将止转件持续地弹压向中介件的蓄能弹簧。而闩锁机构则包括触发件，其可转动地和至少间接地设置在摩擦件上，被触发机构触发之前，该触发件可维持与止转件至少间接的卡合，以持续阻止止转件的移动，被触发机构触发之后，该触发件将解除其与止转件的卡合。 Further, the latching mechanism has a planetary combination wheel rotatably disposed on the force limiting member, the portion of the inner portion of the force limiting member fixed to the planetary gear of the partial gear tooth of the support member, which is located at the force limiting a portion of the outer portion of the component is fixed with a locking member; and a trigger member rotatably disposed on the force limiting member, the trigger member can maintain the engagement with the locking member to be continuously blocked before being triggered by the triggering mechanism The rotation of the locking member is released, and after being triggered by the triggering mechanism, the trigger member will release its engagement with the locking member. Another refinement is that the operating mechanism includes a frictional anti-rotation mechanism having at least one anti-rotation member that is non-rotatably and at least indirectly disposed on the friction member for controlled frictional contact with the interposer, and The rotation stop is continuously biased against the energy storage spring of the intermediate member. The latching mechanism includes a triggering member that is rotatably and at least indirectly disposed on the friction member, and the trigger member maintains at least indirect engagement with the rotation preventing member to continuously stop the rotation preventing member before being triggered by the trigger mechanism. After the trigger is triggered by the trigger mechanism, the trigger will release its engagement with the rotation stop.

可选地，还可设置两个径向上相互嵌套的转动导向机构和至少一个弹性元件。该两机构的两个导向件以及两个中介件，以导向面位于同方向端面上的形式，分别连接成刚性一体，以及不可旋转地连接成周向一体；该两个转动导向机构中各自导向摩擦副的升角 λ , 分别大于零且小于等于 ζ , 以及大于 ζ且小于等于 ξ；弹性元件则轴向上至少间接地抵触至升角 λ大于零且小于等于 ζ的所述转动导向机构。 Alternatively, two rotational guiding mechanisms and at least one elastic element that are radially nested with each other may be provided. The two guiding members of the two mechanisms and the two intermediate members are respectively formed in the form of the guiding faces on the same direction end faces, respectively connected to be rigidly integrated, and non-rotatably connected to be circumferentially integrated; respectively, the two rotating guiding mechanisms are respectively guided The rising angle λ of the friction pair is greater than zero and less than or equal to ζ, and greater than ζ and less than or equal to ξ; the elastic element axially at least indirectly interferes with the turning guide mechanism having an angle of rise λ greater than zero and less than or equal to ζ.

再一种再改进是，操动机构包括圓柱凸轮机构，或周向限位机构，该两个机构均具有至少一个凸起，以及可对应地收纳该凸起的凹槽，两者至少间接地分别设置在中介件和导向件中的一个之上，以及与其中的另一构件不可旋转相连的移动件之上；该两个机构均还具有至少一个蓄能弹簧，其用于将移动件持续地弹压向可以致使中介件入楔的方向；而当凸起收纳至凹槽时，中介件在两个圓周方向上均不能自由地入楔。 Still another improvement is that the operating mechanism includes a cylindrical cam mechanism, or a circumferential limiting mechanism, each of the two mechanisms having at least one protrusion, and correspondingly receiving the raised groove, at least indirectly Provided on one of the intermediate member and the guide member, respectively, and on the moving member that is non-rotatably connected to the other member; the two mechanisms each have at least one energy storage spring for continuing the moving member The ground biasing direction can cause the intermediate member to enter the wedge direction; and when the projection is received into the recess, the intermediate member cannot be freely wedged in both circumferential directions.

需要特别说明的是，本申请文件中的相关概念或名词的含义如下：间接地设置：设置在与设置的目的地构件不可旋转相连的其它构件上。转动导向机构：将圓周相对转动转换为至少包括轴向相对移动或移动趋势的导向机构。例如螺旋升角严格一致和不严格一致的滑动 /滚动式螺旋或部分螺旋机构、径向销槽机构、端面楔形机构、端面嵌合机构、端面棘轮机构及圆柱 / 端面凸轮机构。 It should be specially noted that the relevant concepts or nouns in this application have the following meanings: Inter-ground setting: Set on other components that are not rotatably connected to the set destination component. Rotating guide mechanism: Converts the circumferential relative rotation into a guiding mechanism including at least an axial relative movement or movement tendency. For example, a sliding/rolling spiral or partial screw mechanism, a radial pin groove mechanism, an end face wedge mechanism, an end face fitting mechanism, an end face ratchet mechanism, and a cylindrical/end face cam mechanism with a strictly uniform and non-rigid spiral angle.

空间楔形机构：由转动导向机构和牵引摩擦机构组成的机构。 Space wedge mechanism: A mechanism consisting of a rotary guide mechanism and a traction friction mechanism.

入楔：也称楔合，与解楔 /去楔相反，就是中介件 90将导向件 50与摩擦件 70可驱动地连接 /结合成一个摩擦体的工作过程和状态。 Wedge: Also known as wedge, as opposed to wedge/wrap, is the working process and state in which the interposer 90 is drivingly coupled/combined with the friction member 70 into a friction body.

ζ和 ξ : 空间楔形机构的重要极限角，如图 2、 4Α所示的中介件 90 , —方面通，过其摩擦面例如 104与摩擦件 70的牵引摩擦面 72至少轴向抵触，以形成抵触部位的法向压力的合力 W不垂直于回转轴线 X的回转型牵引摩擦机构 F 1 的至少包括一个的一组牵引摩擦副；另一方面，通过其朝向某一圓周方向的导向面例如 94a，与导向件 50的相应导向面例如 54a至少轴向 ·!氏触，以形成 4氐触部位的法向压力的合力 N不垂直于回转轴线 X的转动导向机构 G的至少包括一个的一组导向摩擦副；该抵触部位的公切线与垂至于回转轴线 X的平面的夹角的平均值，称为该抵触部位的升角 λ ; 再一方面，通过其它表面还可作用有诸如用于弹性预紧或限位的其它作用力，参见图 2、 5 ~ 8；在转动导向机构 G 的转动导向工况中，也就是导向件 50致使中介件 90沿例如箭头 Ρ所指方向以大于等于零的速度相对摩擦件 70转动的工况中，能够确保导向摩擦副自锁的双方表面抵触部位的最小升角被定义为 ζ , 而最大升角则被定义为。而该两个极限角则完全界定了中介件 90相对导向件 50向前转动、静止不动和向后转动的一切可能的运动形式。具体含义如下： ζ and ξ: the important limit angle of the space wedge mechanism, as shown in Figs. 2 and 4, the intermediate member 90, through the friction surface, for example, 104 and the traction friction surface 72 of the friction member 70 at least axially interfere with each other to form The resultant force of the normal pressure of the abutting portion W is not perpendicular to the swivel axis X of the rotary traction friction mechanism F 1 and includes at least one set of traction friction pairs; on the other hand, the guide surface passing through a circumferential direction thereof, for example, 94a And a corresponding guiding surface of the guiding member 50, for example, 54a, at least axially contacted to form a combined force of the normal pressures of the four contact portions N, which is not perpendicular to the rotation axis X, and includes at least one of the rotating guiding mechanisms G The guiding friction pair; the average value of the angle between the common tangent of the abutting portion and the plane perpendicular to the axis of rotation X is called the rising angle λ of the abutting portion; on the other hand, the other surface may also act, for example, for elasticity. Other forces for pretensioning or limiting, see Figures 2, 5-8; In the rotational guiding condition of the turning guide G, that is, the guiding member 50 causes the intermediate member 90 to be greater than or equal to the direction indicated by, for example, the arrow Ρ In the case where the zero speed is rotated with respect to the friction member 70, the minimum angle of elevation that can ensure that the surface frictional portions of the guide friction pair are self-locking is defined as ζ, and the maximum angle of elevation is defined as. And the two The limit angle then fully defines all possible forms of motion of the intermediate member 90 relative to the guide member 50 for forward rotation, stationary motion and rearward rotation. The specific meaning is as follows:

1、当 ξ < λ < 90度时，导向摩擦副和牵引摩擦副均不能自锁，通过导向摩擦副的法向压力 Ν，或者其分力 Q和 Τ，导向件 50可致使中介件 90相对其向前亦即箭头 Ρ所指方向滑转 /挤出。因此，导向件 50与摩擦件 70不能被中介件 90楔合成一个摩擦体。只是由于压力 Ν源自非弹性力，或者源自弹性力但受构件结构所限，才致使中介件 90仅被导向件 50推动着相对摩擦件 70摩擦滑转而未被实际挤出。 1. When ξ < λ < 90 degrees, neither the guiding friction pair nor the traction friction pair can be self-locking. By the normal pressure 导向 of the guiding friction pair, or its component forces Q and Τ, the guiding member 50 can cause the intermediate member 90 to be opposite. It slides/extrudes forward in the direction indicated by the arrow Ρ. Therefore, the guide member 50 and the friction member 70 cannot be wedged into a friction body by the intermediate member 90. Only because the pressure Ν originates from the non-elastic force, or originates from the elastic force but is limited by the structure of the member, the intermediate member 90 is only urged by the guide member 50 to frictionally slip relative to the friction member 70 without being actually extruded.

2、当 ζ < λ ξ且 λ > 0时，导向摩擦副处于恒定的自锁状态，牵引摩擦副处于不可自锁的一般静摩擦状态。此时，空间楔形机构的传动能力唯一决定于楔合时牵引摩擦副的牵引摩擦转矩。因此，尽管中介件 90 可以将导向件 50 与摩擦件 70楔合成一个摩擦体，但在摩擦件 70相对导向件 50过载时，牵引摩擦副仍可由静摩擦状态自然地转入滑动摩擦状态而导向摩擦副仍可维持自锁。对应地，空间楔形机构处于半楔合状态，紧急制动装置处于非完全接合状态。 2. When ζ < λ ξ and λ > 0, the guiding friction pair is in a constant self-locking state, and the traction friction pair is in a general static friction state that cannot be self-locking. At this time, the transmission capacity of the space wedge mechanism is uniquely determined by the traction friction torque of the traction pair when wedged. Therefore, although the intermediate member 90 can wedge the guide member 50 and the friction member 70 into a friction body, when the friction member 70 is overloaded relative to the guide member 50, the traction friction pair can be naturally transferred from the static friction state to the sliding friction state to guide the friction. The assistant can still maintain self-locking. Correspondingly, the space wedge mechanism is in a half-wedge state and the emergency brake device is in a non-fully engaged state.

3、当 0 < λ ζ (针对 ζ > 0 的情况）时，牵引摩擦副处于恒定的自锁状态，导向摩擦副处于一般静摩擦状态。空间楔形机构的传动能力唯一决定于楔合时导向摩擦副的最大静摩擦转矩 /导向摩擦转矩。因此，尽管中介件 90可以将导向件 50与摩擦件 70楔合成一个摩擦体，但在摩擦件 70相对导向件 50过载时，中介件 90将具有突破导向摩擦副的最大静摩擦状态而相对导向件 50滑转爬升的趋势，只是该爬升趋势可被楔形机构的刚性轴向力封闭结构所阻止（除非压力 Ν源自弹性力），所以，导向摩擦副可被强制性地维持在等同于自锁的一般静摩擦状态。即，中介件 90、导向件 50与摩擦件 70三者被强制楔合 /结合成一个转动整体，即使过载至毁损也不相互滑转爬升。空间楔形机构因而处于类似斜撑式超越离合器的绝对自锁 /楔合状态，其传动能力仅决定于结构强度。 3. When 0 < λ ζ (for ζ > 0), the traction friction pair is in a constant self-locking state, and the guiding friction pair is in a general static friction state. The transmission capacity of the space wedge mechanism is uniquely determined by the maximum static friction torque/guide friction torque of the guide friction pair when wedged. Therefore, although the intermediate member 90 can wedge the guide member 50 and the friction member 70 into a friction body, when the friction member 70 is overloaded relative to the guide member 50, the intermediate member 90 will have the maximum static friction state of the breakthrough guide friction pair and the relative guide member. The tendency of the 50-sliding climb is that the climbing trend can be prevented by the rigid axial force-closed structure of the wedge mechanism (unless the pressure Ν is derived from the elastic force), so the guide friction pair can be forcibly maintained at the same level as the self-locking The general static friction state. That is, the intermediate member 90, the guide member 50 and the friction member 70 are forcibly wedged/combined into a single rotating body, and they do not slip and climb each other even if they are overloaded to be damaged. The space wedge mechanism is thus in an absolute self-locking/wedge state similar to a slanted overrunning clutch, the transmission capacity of which is determined solely by the structural strength.

由常识可知， λ等于 ζ的情况，只存在于理论上而不存在于现实中。也就是说，因不能同时自锁而必然始终存在着一组不自锁的可滑转摩擦副，（空间 ) 楔形机构传递转矩的物理本质只能是摩擦，而不是现有技术认定的摩擦自锁。 It is common knowledge that the case where λ is equal to ζ exists only in theory and not in reality. That is to say, because there is always a set of non-lockable frictional friction pairs that cannot be self-locking at the same time, the physical nature of the (space) wedge mechanism transmitting torque can only be friction, instead of the friction determined by the prior art. Self-locking.

显然，上述升角 λ就是空间楔形机构的楔角，也称楔合角 /挤住角，并且仅在 0 < λ < ξ时，空间楔形机构方可楔合，紧急制动装置方可接合。 Obviously, the above-mentioned rising angle λ is the wedge angle of the space wedge mechanism, also called the wedge angle/crowding angle, and only when 0 < λ < ,, the space wedge mechanism can be wedged, and the emergency braking device can be engaged.

相对现有技术的紧急制动装置，依据本发明的空间楔合式紧急制动装置，因基于可循环回转的空间楔合式摩擦制动机理而具有封装的独立结构，以及因此而与使用环境与对象基本无关的优异的适用性，因省去了诸如限速器***等而大幅简化了整体结构，降低了所占用空间和制作成本，简化了操作程序，同时具有更高的可靠性和更高的安全性。借助下述实施例的说明和附图，本发明的目的和优点将显得更为清楚和明了。附图说明 Compared with the prior art emergency braking device, the space-wedge emergency braking device according to the present invention has a packaged independent structure due to the space-wrap friction braking mechanism based on the revolving rotation, and thus the environment and objects The extremely unsuitable superior applicability greatly simplifies the overall structure by eliminating the need for a speed limiter system, reduces the space occupied and manufacturing costs, simplifies the operating procedure, and has higher reliability and higher safety. The objects and advantages of the invention will be apparent from the description and appended claims. DRAWINGS

图 1是应用本发明的电梯***布局的筒化示意图。 BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic view showing the layout of an elevator system layout to which the present invention is applied.

图 2是根据本发明的实施例一的紧急制动装置的轴向剖面图。 Figure 2 is an axial sectional view of an emergency brake device according to a first embodiment of the present invention.

图 3是以图 2的左视图视角表示的轴向力封闭式袋形摩擦件的端面示意图。图 4 A ~ 4B分别是图 2中各机构的齿廓向同一外圓柱面径向投影的局部展开图，图 4A对应于双向制动，图 4B对应于单向制动。 Figure 3 is a schematic side view of the axial force-closed bag-shaped friction member shown in the left side view of Figure 2; 4A to 4B are partial development views respectively showing the radial profile of the tooth profile of each mechanism of Fig. 2 toward the same outer cylindrical surface, Fig. 4A corresponds to bidirectional braking, and Fig. 4B corresponds to one-way braking.

图 5是根据本发明的实施例二的紧急制动装置的简化的轴向剖面图。 Figure 5 is a simplified axial cross-sectional view of an emergency braking device in accordance with a second embodiment of the present invention.

图 6是图 5的右视图的局部示意图。 Figure 6 is a partial schematic view of the right side view of Figure 5.

图 Ί是根据本发明的实施例三的紧急制动装置的简化的轴向剖面图。 Figure Ί is a simplified axial cross-sectional view of an emergency braking device in accordance with a third embodiment of the present invention.

图 8是根据本发明的实施例四的紧急制动装置的简化的轴向剖面图。具体实施方式 Figure 8 is a simplified axial cross-sectional view of an emergency braking device in accordance with a fourth embodiment of the present invention. detailed description

必要说明：本说明书的正文及所有附图中，相同或相似的构件及特征部位均采用相同的附图标记，并只在它们第一次出现时给予必要说明。同样，也不重复说明相同或相似机构的工作机理或过程。为区别设置在对称或对应位置上的相同的构件或特征部位，本说明书在其附图标记后面附加了字母，而在泛指说明或无需区别时，则不附加任何字母。 Necessary description: In the text of the specification and all the drawings, the same or similar components and features are denoted by the same reference numerals, and the necessary descriptions are given only when they appear for the first time. Similarly, the working mechanism or process of the same or similar institutions is not repeated. In order to distinguish the same members or feature parts set at symmetrical or corresponding positions, the present specification appends letters to the reference numerals, and does not attach any letters when it is generally indicated or does not need to be distinguished.

实施例一：对中限位式紧急制动装置 B1 Embodiment 1: Centering emergency brake device B1

参见图 1 , 在电梯轿厢 200和 /或对重（未示出）的上部顶面或下部底面上，最佳地固定设置有两套紧急制动装置 Bl。该两个装置 B1 向外端延伸出的传动轴 210 , 穿过固定设置在轿厢 200上的轴承座 204 , 分别抵达两侧的齿条式导轨 202侧面，并通过固定于其端部的随动齿轮 110, 与该导轨 202可靠啮合。最佳地，还设置有公知的靠背轮（未示出），以确保该啮合的可靠。另外，曳引轿厢 200上下运动的曳引钢绳 216，依次穿过固定在前者顶面中央的承力座 206，以及位于其内的诸如碟簧或膜片弹簧之类的弹性元件 230, 固结于承力圓盘 218的中央。这样，断绳的瞬间，处于被压缩状态的该蓄能弹性元件 230 的复原力，便可驱动其下方的承力圓盘 218位移，从而借助与承力圓盘 218 固结的感应钢丝拉绳 208, 致动紧急制动装置 B1 , 于断绳之际制停轿厢 200。实际上，如后所述，紧急制动装置 B1 也可以应用于例如自动扶梯中，以滑靴的重力 /弹力转矩为致动力来应对驱动链条的断开和过度松弛的需要紧急制动的情况。 Referring to Fig. 1, two sets of emergency brake devices Bl are optimally fixedly disposed on the upper top surface or the lower bottom surface of the elevator car 200 and/or the counterweight (not shown). The drive shaft 210 extending from the two ends of the two devices B1 passes through the bearing housing 204 fixedly disposed on the car 200, and respectively reaches the sides of the rack-type guide rails 202 on both sides, and is fixed by the end portion thereof. The moving gear 110 is in reliable engagement with the guide rail 202. Most preferably, a known back wheel (not shown) is provided to ensure reliable engagement. In addition, the traction wire 216 that moves the car 200 up and down moves through the bearing seat 206 fixed in the center of the top surface of the former, and the elastic member 230 such as a disc spring or a diaphragm spring located therein. Consolidated in the center of the bearing disc 218. Thus, at the moment of breaking the rope, the restoring force of the energy storage elastic member 230 in the compressed state can drive the bearing disk 218 underneath to be displaced, thereby pulling the rope by the induction wire consolidated with the bearing disk 218. 208. Actuate the emergency brake device B1 to stop the car 200 when the rope is broken. In fact, as will be described later, the emergency brake device B1 can also be applied to, for example, an escalator, with the gravity/elastic torque of the shoe as the actuation force to cope with the need for emergency braking of the drive chain to be disconnected and excessively slackened. Happening.

以下为了说明的简便，假定图 1中的两个紧急制动器 B1完全相同参见图 2。紧急制动装置 B1主要具有作为执行部分的制动机构，以及作为控制部分的操动机构和触发机构 AC：。其中，制动机构是一个空间楔合式摩擦机构，其具有最佳地绕轴线 X形成并最佳地呈至少大致环状的导向件 50、摩擦件 70、中介件 90和阶梯状传动轴 210。导向件 50的内端面上，设置有一组最佳地绕轴线 X周向均布的双向螺旋导向齿 52, 其内环侧朝内端延伸的管状基体 60 的内周面上，最佳地设置有内花键齿，以与同轴线地设置在其内孔中的传动轴 210借助花键副不可旋转地相连。传动轴 210的轴头部最佳地借助轴承 158定位在内周面 84a上，其阶梯状凸缘 214a则可滑动地定位在内周面 84b上。传动轴 210,最佳地由阶梯状凸缘 214a—端延伸至导轨 202, 以固定安装随动齿轮 110。中介件 90可滑转地设置在管状基体 60的外周面上，其直接面对导向件 50的端面上，设置有与导向齿 52呈互补式构造且相互恒久地嵌合在一起的一组螺旋导向齿 92, 以构成最佳地绕轴线 X回转的面接触型双向转动导向机构 G。 For the sake of simplicity of explanation, it is assumed that the two emergency brakes B1 in Fig. 1 are identical. See Fig. 2. The emergency brake device B1 mainly has a brake mechanism as an execution portion, and an operation mechanism and a trigger mechanism AC as a control portion. Among other things, the brake mechanism is a space-wedge friction mechanism having guide members 50, friction members 70, intermediate members 90 and stepped drive shafts 210 that are optimally formed about the axis X and are preferably at least substantially annular. The inner end surface of the guide member 50 is provided with a plurality of bidirectional helical guide teeth 52 which are uniformly distributed circumferentially around the axis X, and an inner circumferential surface of the tubular base body 60 whose inner ring side extends toward the inner end is optimally disposed. The spline teeth are non-rotatably connected by means of spline pairs to the drive shaft 210 which is arranged coaxially in its inner bore. The shaft head of the drive shaft 210 is preferably positioned on the inner peripheral surface 84a by means of a bearing 158, and its stepped flange 214a is slidably positioned on the inner peripheral surface 84b. The drive shaft 210, preferably extending from the stepped flange 214a end to the rail 202, securely mounts the follower gear 110. The intermediate member 90 is slidably disposed on the outer peripheral surface of the tubular base body 60, and directly faces the end surface of the guide member 50, and is provided with a set of spirals which are complementary to the guide teeth 52 and are rigidly fitted to each other. The guide teeth 92 are configured to constitute a surface contact type bidirectional rotation guide mechanism G that is optimally rotated about the axis X.

再结合图 3进行说明。为具备轴向力封闭功能和便于安装，摩擦件 70被最佳地设置成方形袋形构件，其绕轴线 X形成的内周面 84的轴向中部，同轴线地设置有最佳地为平面型的盘形环状周向凹槽 78。该周向凹槽 78的约半周的内表面，最佳地沿两相互平行的切线方向 H和 H'延伸至摩擦件 70的外表面 88, 并形成等截面矩形入口 82。周向凹槽 78的径向内表面 80，因而延伸成具有 U字形横截面形状的非闭合式内径向表面。相互嵌合并安装好弹性元件 150 的导向件 50和中介件 90, 可由入口 82直接纳入周向凹槽 78 , 并被轴向贯穿于摩擦件 70内孔中的传动轴 210径向定位。摩擦件 70的底部，例如径向上背离入口 82 的一端，设置有可借助螺拴等固定连接至轿厢 200的包括有一组安装孔 83的板状连接凸缘 86。当然，该凸缘 86也可设置在摩擦件 70的端面上，摩擦件 70因此可呈圓环形状。 This will be described in conjunction with FIG. 3. In order to have an axial force closing function and easy installation, the friction member 70 is the most Preferably, it is provided as a square bag-shaped member whose axially central portion of the inner peripheral surface 84 formed around the axis X is coaxially provided with a disk-shaped annular circumferential groove 78 which is optimally planar. The inner surface of the circumferential groove 78 is preferably extended to the outer surface 88 of the friction member 70 in two mutually parallel tangential directions H and H' and forms an equal-section rectangular inlet 82. The radially inner surface 80 of the circumferential groove 78 thus extends into a non-closed inner radial surface having a U-shaped cross-sectional shape. The guide member 50 and the intermediate member 90, which are fitted to each other and are fitted with the elastic member 150, can be directly inserted into the circumferential groove 78 by the inlet 82 and radially positioned by the drive shaft 210 axially inserted through the bore of the friction member 70. The bottom of the friction member 70, for example, one end radially away from the inlet 82, is provided with a plate-like connecting flange 86 including a set of mounting holes 83 that can be fixedly coupled to the car 200 by means of a thread or the like. Of course, the flange 86 can also be disposed on the end face of the friction member 70, and the friction member 70 can thus have a circular ring shape.

实际上，轴向力封闭的袋形摩擦件 70也可以是一个组合构件。例如，借助诸如焊接、铆接、螺栓或过盈地设置至少一个环形箍之类的紧固连接方式，通过轴向对接或径向对接，将两个设置有中心圓孔、或两个至少大致对称的半圓壳式限力元件，紧固成如图 2所示的摩擦件 70。相关结构的更详细说明和图示，可参见上文所整体结合的两项专利申请，此处不作进一步说明。 In fact, the axially closed bag-shaped friction member 70 can also be a composite member. For example, by means of a fastening connection such as welding, riveting, bolting or providing at least one annular hoop, the two are provided with a central circular hole, or two at least substantially symmetrical by axial or radial butt joints. The semicircular shell force limiting element is fastened to a friction member 70 as shown in FIG. For a more detailed description and illustration of related structures, reference is made to the two patent applications incorporated by reference in its entirety herein.

继续参见图 2，周向凹槽 78分别设置有回转型牵引摩擦面 72和传力摩擦面 74。其左端的牵引摩擦面 72, 与设置在中介件 90无齿端面上的回转摩擦面 104 摩擦相连，构成回转型面接触牵引摩擦机构 Fl。其右端的传力摩擦面 74, 与设置在导向件 50无齿端面的传力摩擦面 58摩擦相连，构成可与导向件 50直接传递摩擦转矩的回转型面接触传力摩擦机构 F2。牵引摩擦机构 F1和转动导向机构 G, 共同组成端面型空间楔形机构，该机构再与传力摩擦机构 F2—起，构成紧急制动装置 B1的轴向力封闭的空间楔合式双向摩擦 /制动机构。 Continuing to refer to Fig. 2, the circumferential groove 78 is provided with a rotary traction friction surface 72 and a force transmitting friction surface 74, respectively. The traction friction surface 72 at the left end thereof is frictionally connected with the rotary friction surface 104 provided on the toothless end surface of the intermediate member 90 to constitute a rotary surface contact traction friction mechanism F1. The force transmitting friction surface 74 at the right end thereof is frictionally connected with the force transmitting friction surface 58 provided on the toothless end surface of the guide member 50, and constitutes a rotary type surface contact force transmitting friction mechanism F2 which can directly transmit the friction torque with the guide member 50. The traction friction mechanism F1 and the rotation guide mechanism G together form an end-face type space wedge mechanism, which in turn is combined with the force-transmitting friction mechanism F2 to constitute a space-wound type bidirectional friction/braking of the axial braking force of the emergency braking device B1. mechanism.

应该指出的是，本申请 "直接传递摩擦转矩" 的含义是指，转矩在两构件间的传递路径仅经过一个摩擦机构，而不经过任何第二个其它机构，其与该摩擦机构所具有的摩擦面 /片的数量没有任何关系。 It should be noted that the meaning of "direct transfer friction torque" in the present application means that the transmission path of torque between the two members passes through only one friction mechanism without passing through any second other mechanism, and the friction mechanism There is no relationship to the number of friction surfaces/sheets.

应该注意的是，鉴于全周向面接触摩擦的特点，紧急制动装置 B1中应最佳地加注有助于散热的制动液或冷却液，以形成湿式摩擦环境。同时，还应在摩擦件 70等构件的摩擦表面或内部，参照公知技术，最佳地设置相应的彼此连通的径向通道。相应地，应以诸如焊接、铆接、胶接、径向螺钉之类的紧固或非紧固连接方式，将用于封住入口 82的封口件 190, 设置在摩擦件 70的开口表面 88上。并对其它相关部位也予以密封。例如，给轴承 158附装上未示出的密封圈或轴承盖。 It should be noted that in view of the full-face contact friction characteristics of the entire circumference, the emergency brake device B1 should be optimally filled with brake fluid or coolant which contributes to heat dissipation to form a wet friction environment. At the same time, corresponding radial passages communicating with each other should be optimally provided on the friction surface or inside of the member such as the friction member 70, in accordance with known techniques. Accordingly, the closure member 190 for sealing the inlet 82 should be disposed on the open surface 88 of the friction member 70 by a fastening or non-fastening connection such as welding, riveting, gluing, radial screwing or the like. . It also seals other related parts. For example, a seal or bearing cap, not shown, is attached to the bearing 158.

显然，由于袋形摩擦件 70的盘形环状周向凹槽 78被最佳地设置成平盘状而非锥盘状，因此，制动装置 B1在理论上可以不要求导向件 50和中介件 90的组合与摩擦件 70之间的同轴度精度。也就是说，可以不对制动装置 B1 中的转动导向机构 G、牵引摩擦机构 F1和传力摩擦机构 F2三者之间以及三者与轴线 X 的同轴度提出专门的要求，只要其两个面接触回转摩擦副垂直于轴线 X，以及仅具有几乎不可察觉的相对转动的导向件 50和中介件 90相互间同轴线设置即可。而相对现代工艺，保证该两个环状构件之间的同轴度又是一件简单和低成本的劳动。因此，这将显著降低制作、装配和使用制动装置 B1的要求和成本，显著优越于完全相反的现有楔合技术。 Obviously, since the disc-shaped annular circumferential groove 78 of the bag-shaped friction member 70 is optimally arranged in a flat disk shape instead of a conical disk shape, the brake device B1 may theoretically not require the guide member 50 and the intermediate member 90. The accuracy of the coaxiality between the combination and the friction member 70 is combined. That is to say, special requirements may be imposed on the coaxiality between the rotary guide mechanism G, the traction friction mechanism F1 and the force-transmitting friction mechanism F2 in the brake device B1 and the three axes with the axis X, as long as they are two The surface contact rotary friction pair is perpendicular to the axis X, and the guide member 50 and the intermediate member 90 having only relatively imperceptible relative rotation are disposed coaxially with each other. Relative to modern processes, ensuring the coaxiality between the two annular members is a simple and low-cost labor. Therefore, this will significantly reduce the requirements and costs of manufacturing, assembling and using the brake device B1, Significantly superior to the exact opposite existing wedge technology.

还应指出的是，周向凹槽 78呈环状和入口 82呈等截面矩形，均是实现本发明的最佳但并非必需设置。实际上，只要能够纳入诸如导向件 50和中介件 90 , 周向凹槽 78和入口 82可以具有任意形状和不等截面。比如，周向凹槽 78可以呈矩形，入口 82可因两个延伸切线方向 H和 H'不相互平行而呈扩口喇叭形。同样道理，摩擦件 70的内周面 84也不必需周向封闭和对应于贯通式内孔，其完全可以呈例如大致半周的 U形开口状并对应于一个盲孔，只要在该内周面 84上可以设置出用以收纳诸如中介件 90之类的回转构件的大致半周的周向凹槽 78 即可。 It should also be noted that the circumferential groove 78 is annular and the inlet 82 is rectangular in equal cross-section, which is the best but not required arrangement for carrying out the invention. In fact, the circumferential groove 78 and the inlet 82 may have any shape and unequal section as long as they can be incorporated, such as the guide 50 and the intermediate member 90. For example, the circumferential groove 78 may have a rectangular shape, and the inlet 82 may have a flared flare shape because the two extended tangential directions H and H' are not parallel to each other. By the same token, the inner circumferential surface 84 of the friction member 70 does not have to be circumferentially closed and corresponds to the through-type inner hole, which may completely have a U-shaped opening shape of, for example, substantially a half circumference and corresponds to a blind hole as long as it is on the inner circumferential surface. A substantially half-circumferential circumferential groove 78 for accommodating a rotary member such as the interposer 90 may be provided on the 84.

另外，如果需要，摩擦件 70也可以是周向非完整的袋形构件。即，当需要轴向延伸例如导向件 50的管状基体 60以致其不能径向通过入口 82时，可在入口 82处的轴向一端设置径向缺口。例如，将位于内周面 84b—端的正好半周的内周面，沿平行于 H或 H'的两条相互平行的切线方向，径向延伸至摩擦件 70 的外表面 88 , 并形成一个允许管状基体 60置入 /通过的缺口。于是，内周面 84b 同样延伸成具有 U字形横截面形状的非闭合式内径向表面，摩擦件 70变成为一个形似砝码的 U形开口件。当然，此时应在扩大的入口 82中最佳地设置一个与该入口具有互补式构造的弧形压件，以径向定位管状基体 60。 Additionally, the friction member 70 can also be a circumferentially non-hollow pocket member if desired. That is, when it is desired to axially extend the tubular base 60 such as the guide member 50 such that it cannot pass through the inlet 82 radially, a radial notch can be provided at one axial end of the inlet 82. For example, an inner peripheral surface of exactly half a circumference of the inner peripheral surface 84b is radially extended to the outer surface 88 of the friction member 70 in two mutually parallel tangential directions parallel to H or H', and an allowable tubular shape is formed. The gap in which the substrate 60 is placed/passed. Thus, the inner peripheral surface 84b also extends into a non-closed inner radial surface having a U-shaped cross-sectional shape, and the friction member 70 becomes a U-shaped opening member which is shaped like a weight. Of course, an arcuate press member having a complementary configuration with the inlet is preferably provided in the enlarged inlet 82 to radially position the tubular base 60.

有关轴向力封闭结构及袋形构件的更多变型的图示和说明，可参见上文所整体结合的两项专利申请，以及本申请人提出的名为具有袋形构件的空间楔合式摩擦超越离合器，并全文结合于此的中国专利申请 201020563404.9，本申请不作进一步说明。 For a diagram and description of more variations of the axial force closure structure and the pocket member, reference is made to the two patent applications incorporated by reference above, and the space wedge friction friction proposed by the Applicant as having a pocket member. Chinese Patent Application No. 201020563404.9, which is incorporated herein by reference.

虽然依靠周向惯性或者依靠 0 < λ ζ的升角 λ的特别设置均可致使中介件 90入楔，但为确保摩擦 /制动机构快速和可靠地楔合，紧急制动装置 B1还最佳地设置有弹性预紧机构。该机构主要包括一个螺旋压簧式预紧用弹性元件 150 , 其套设在转动导向机构 G的外周面上，并分别抵触至导向件 50与中介件 90两者外周面外端的径向凸缘，参见图 2。这样，借助摩擦件 70相对中介件 90 的转动，牵引摩擦机构 F1可建立起持续的摩擦连接关系和相应牵引转矩，可在第一时刻牵引着中介件 90完成入楔动作。 Although the intervening member 90 can be wedged by means of circumferential inertia or by a special setting of the angle λ of 0 < λ ,, the emergency brake B1 is also optimal for ensuring a quick and reliable wedge of the friction/braking mechanism. An elastic pretensioning mechanism is provided. The mechanism mainly includes a spiral compression spring type pretensioning elastic member 150 which is sleeved on the outer circumferential surface of the rotation guiding mechanism G and respectively abuts against the radial flange of the outer peripheral surface of both the guiding member 50 and the intermediate member 90. , see Figure 2. Thus, by the rotation of the friction member 70 relative to the intermediate member 90, the traction friction mechanism F1 can establish a continuous frictional connection relationship and a corresponding traction torque, and the intermediate member 90 can be pulled at the first moment to complete the wedge action.

下面再结合图 4Α来说明转动导向机构 G的详细关系和结构特征。其中，最佳地具有梯形横截面且径向延伸的每对端面型螺旋导向齿 52和 92的相互面对的导向面 54和 94 , 均被互补地构造成螺旋型齿面，两者周向相互贴合后，便可形成对应于不同圓周方向的两组面接触的螺旋式导向摩擦副。优选地，分别朝向两个圓周方向的两组导向面 54a和 94a以及 54b和 94b的两个互补的升角 λ _a和 X _b , 均对称地等于 λ。并且一般地， 0 < λ ξ , 允许过载打滑时， ζ < λ < ξ , 绝对不许打滑时， 0 < λ ζ (当 ζ > 0 )。显然，如果只需传递单向转矩，升角 λ ^ λ ι^中的一个，可以最佳地等于平行于轴线 X的 90度。例如，将其中的一组导向面 54b和 94b，设置成最佳地平行于轴线 X的非导向面 56和 96，以保证双方周向抵触时不会导致楔合，参见图 4B。优选地，所有导向齿 52a和 92a 的齿高，均被设置成不妨碍对应于两个圓周方向的两组导向面 54a和 94a以及 54b和 94b在轴向上的同时贴合，亦即各自的齿顶与各自所处齿槽槽底面的轴向最小间距 δ最佳地大于零，以保证转动导向机构 G的周向自由度 /间隙可以等于令。 The detailed relationship and structural features of the rotary guide mechanism G will be described below with reference to FIG. Wherein, the mutually facing guide faces 54 and 94 of each pair of end face-type helical guide teeth 52 and 92 which preferably have a trapezoidal cross section and which extend radially are complementarily configured as spiral-shaped tooth faces, both of which are circumferential After being bonded to each other, a pair of surface-contacting spiral guide friction pairs corresponding to different circumferential directions can be formed. Preferably, the two complementary elevation angles λ _a and X _b of the two sets of guide faces 54a and 94a and 54b and 94b, respectively facing the two circumferential directions, are symmetrically equal to λ. And generally, 0 < λ ξ , when overload slip is allowed, ζ < λ < ξ , when absolutely no slip, 0 < λ ζ (when ζ > 0). Obviously, if only one-way torque is to be transmitted, one of the rising angles λ ^ λ ι^ can be optimally equal to 90 degrees parallel to the axis X. For example, one of the sets of guide faces 54b and 94b is disposed to be non-guide faces 56 and 96 that are optimally parallel to the axis X to ensure that the two sides do not cause wedging when circumferentially opposed, see FIG. 4B. Preferably, the tooth heights of all the guide teeth 52a and 92a are set so as not to hinder the simultaneous engagement of the two sets of guide faces 54a and 94a and 54b and 94b corresponding to the two circumferential directions in the axial direction, that is, the respective The axial direction of the tooth tip and the bottom surface of the respective groove groove The minimum spacing δ is optimally greater than zero to ensure that the circumferential freedom/gap of the rotational guiding mechanism G can be equal to the order.

容易理解，导向件 50端面上的多个导向齿 52实际上就是空间楔形机构的楔形齿，其导向面 54分别朝两个圓周方向轴向上逐渐靠近摩擦件 70的回转型牵引摩擦面 72, 并与后者分别围成两组各包括多个的沿周向延伸的端面楔形空间。而设置在该多个楔形空间中的多个导向齿 92就是楔合子，其最佳地相互合并成一个零件，即整体环状的中介件 90。 It is easy to understand that the plurality of guiding teeth 52 on the end surface of the guiding member 50 are actually wedge-shaped teeth of the space wedge mechanism, and the guiding surfaces 54 are gradually axially closer to the rotary traction friction surface 72 of the friction member 70 toward the two circumferential directions. And the latter is respectively divided into two groups of a plurality of circumferentially extending end face wedge-shaped spaces. The plurality of guide teeth 92 disposed in the plurality of wedge-shaped spaces are wedges which are optimally combined with each other into a single piece, i.e., an integrally annular intermediate member 90.

另外，所有导向齿 52和 92的齿高和齿宽，均设置成致使制动装置 B1的，或者说是致使转动导向机构 G中导向件 50与中介件 90的轴向自由度 δ大于等于零，以及周向自由度 ε大于零。因此，当导向件 50与中介件 90处于在两个圓周方向上均不相互抵触的周向相对位置时，空间楔形机构将进入可任意自由转动的工况，对应地，紧急制动装置 B1进入解楔式分离工况。 In addition, the tooth height and the tooth width of all of the guide teeth 52 and 92 are set such that the axial freedom δ of the brake device B1 or the guide member 50 and the intermediate member 90 in the rotary guide mechanism G is greater than or equal to zero. And the circumferential freedom ε is greater than zero. Therefore, when the guide member 50 and the intermediate member 90 are in a circumferentially opposite position that does not interfere with each other in both circumferential directions, the space wedge mechanism will enter an arbitrarily freely rotatable condition, and correspondingly, the emergency brake device B1 enters. Unwrapped separation conditions.

为按需要保持住该分离工况，也就是按需要赋予或撤销空间楔形机构的入楔能力，操动机构包括一个设置在导向件 50与中介件 90之间的周向限位机构 CM, 其具有大于等于零的周向自由度。该机构的至少包括一个的一组限位凸起 68, 是一个由中介件 90内周面内径向地延伸至限位凹槽 118中的径向销。参看图 2、 4A，限位凹槽 118则以大致 V形缺口状的形式，对应地设置在可轴向移动的一组轴向爪 124头部的端面上。该至少为一个的轴向爪 124，最佳地周向均布在限位环 120内径侧的环形端面上，并穿过位于阶梯状凸缘 214a外周面的轴向延伸型缺口，沿传动轴 210 的外周面，可滑动地轴向延伸至设置在管状基体 60相应端面上的轴向延伸的基准槽 126中。限位环 120则套设在凸缘 214a外端阶梯状凸缘 214b的外周面上。 In order to maintain the separation condition as needed, that is, to impart or revoke the wedge function of the space wedge mechanism as needed, the operating mechanism includes a circumferential limiting mechanism CM disposed between the guide member 50 and the intermediate member 90, Has a circumferential freedom of zero or more. The mechanism includes at least one set of limiting projections 68 which are radial pins extending radially into the limiting recesses 118 in the inner peripheral surface of the intermediate member 90. Referring to Figures 2, 4A, the limit recess 118 is in the form of a generally V-shaped notch, correspondingly disposed on the end face of the axially movable set of axial jaws 124. The at least one axial claw 124 is optimally circumferentially distributed on the annular end surface of the inner diameter side of the limiting ring 120, and passes through an axially extending notch located on the outer circumferential surface of the stepped flange 214a along the transmission shaft 210. The outer peripheral surface slidably extends axially into the axially extending reference groove 126 disposed on the respective end surface of the tubular base 60. The retaining ring 120 is sleeved on the outer peripheral surface of the stepped flange 214b at the outer end of the flange 214a.

显然，上述轴向延伸型缺口也可最佳地用作基准槽 126。 It is apparent that the axially extending notch described above can also be optimally used as the reference groove 126.

设置上，周向限位机构 CM各结构要素之间具有这样的效果。即，当限位凹槽 118移至不收纳或收纳限位凸起 68的两个轴向位置时，中介件 90在两个圓周方向上将对应地可以或不可以周向 4氏触至导向件 50, 并被对应地赋予或 ·!款销入楔的能力。该两个轴向位置的最小距离等于 L, 参见图 4A。其中，凹槽 118 最佳地呈对称形状，限位凸起 68在该距离内周向两侧的最大自由度，正好等于 ε /2。而在仅需单向楔合之际，其周向楔合一侧的最大自由度只需大于零即可，参见图 4Β。 In the setting, the circumferential limit mechanism CM has such an effect between the structural elements. That is, when the limiting groove 118 is moved to two axial positions where the limiting projection 68 is not received or received, the intermediate member 90 may or may not be circumferentially guided in two circumferential directions. The piece 50, and correspondingly gives the ability to be driven into the wedge. The minimum distance between the two axial positions is equal to L, see Figure 4A. Wherein, the groove 118 is optimally symmetrical, and the maximum degree of freedom of the limiting protrusion 68 on both sides in the circumferential direction is exactly equal to ε /2. When only one-way weaving is required, the maximum degree of freedom on the circumferential wedge side needs to be greater than zero, see Figure 4Β.

因此，触发机构 AC的任务，就是致动操动机构，以轴向移动限位凹槽 118, 并使其轴向移动距离 L' > L。参见图 2, 触发机构 AC包括一个响应于离心力而动作的离心装置。该离心装置包括至少具有一个的一组扇形连杆 40、连杆 22、离心配重 20和拉簧式限力弹簧 38, 以及环状随动座环 30等。其中，具体为钢球的离心配重 20固定在连杆 22的外端，连杆 22中部的轴向内侧通过铰接销 24, 铰接至位于随动座环 30外周面径向凸耳 32的凹槽中。随动座环 30不可旋转地套设在位于凸缘 214b外端传动轴 210的外周面上，也就是间接地设置在用作转动件的导向件 50上，并被同轴线地设置于其外端的复位弹簧 154和卡环 184弹性限定。扇形连杆 40径向外侧的凹槽通过铰接销 26铰接至连杆 22的内端两侧，其圓心处的耳状凹槽通过铰接销 28铰接至位于限位环 120外周面的径向凸耳两侧。限力弹簧 38连接至随动座环 30和限位环 120双方的任意两点之间，图 2 中连接至铰接销 24和 28的方案显然不是最佳，仅仅为了便于绘图和说明。实际上，限力弹簧 38也可以是分别连接在随动座环 30和限位环 120相对端面上的弹簧片。 Therefore, the task of the trigger mechanism AC is to actuate the operating mechanism to axially move the limit groove 118 and move it axially by a distance L'> L. Referring to Figure 2, the trigger mechanism AC includes a centrifugal device that operates in response to centrifugal force. The centrifugal device includes a set of sector links 40 having at least one, a link 22, a centrifugal weight 20 and a tension spring type force spring 38, and an annular follower ring 30 and the like. Wherein, the centrifugal weight 20 of the steel ball is fixed at the outer end of the connecting rod 22, and the axial inner side of the middle portion of the connecting rod 22 is hinged to the concave portion of the radial lug 32 located on the outer peripheral surface of the follower seat ring 30 by the hinge pin 24. In the slot. The follower seat ring 30 is non-rotatably sleeved on the outer peripheral surface of the drive shaft 210 at the outer end of the flange 214b, that is, indirectly disposed on the guide member 50 serving as a rotating member, and is coaxially disposed thereon. The outer end return spring 154 and the snap ring 184 are elastically defined. The radially outer groove of the sector link 40 is hinged to both sides of the inner end of the link 22 by the hinge pin 26, and the ear groove at the center of the circle is hinged to the radial convex portion located on the outer peripheral surface of the limit ring 120 by the hinge pin 28. Ear two side. The force limiting spring 38 is coupled between any two points of the follower ring 30 and the stop ring 120. The arrangement of the hinge pins 24 and 28 in Fig. 2 is obviously not optimal, merely for ease of drawing and illustration. In fact, the force-limiting springs 38 may also be spring pieces that are respectively connected to the opposite end faces of the follower ring 30 and the limit ring 120.

显然，由公知技术和常识，上述离心装置的几何、质量和弹力等参数可由其转速上限设定值予以对应设定。如图 2上半部所示，当传动轴 210以低于该设定值转动时，借助凸耳 32的凹槽底面 34, 或者促动环 48端面对径向面 42的抵触，铰接销 26位于铰接销 24与 28连线的径向之外的极限位置亦即未触发位置上。离心装置因而稳定地处于未触发状态中，无不必要的振动和磨损，并可长期保持动作的一致性。中介件 90受到限位机构 CM的周向约束，在两个圓周方向上均不能抵触至导向件 50, 更不能入楔。如图 2下半部所示，当传动轴 210 的转速超过该设定值时，作用于离心配重 20 上的离心力，将首先致使连杆 22 开始外径向翻转，接着在极短时间之内克服限力弹簧 38的弹性力并在稍微拉伸该弹簧之后，紧接着致使铰接销 26越过其位于铰接销 24与 28连线上的非稳定临界点，瞬间翻转并抵达其位于该连线径向之内的极限位置亦即触发位置上。离心装置因而处于稳定的触发状态中，限位凹槽 118随限位环 120—同位于轴向最外端位置上，从而解除限位机构 CM对中介件 90的周向约束，令其获得在任意圓周方向上入楔的能力。此时，连杆 22抵触至凸耳 32的凹槽定位斜面 36, 或者，扇形连杆 40的外圓弧面 44抵触至随动座环 30的内端面。 Obviously, the parameters of the geometry, mass and elasticity of the above-mentioned centrifugal device can be correspondingly set by the upper limit of the rotational speed by known techniques and common sense. As shown in the upper half of Fig. 2, when the drive shaft 210 is rotated below the set value, by the groove bottom surface 34 of the lug 32, or the end face of the actuating ring 48 against the radial face 42, the hinge pin 26 is located at an extreme position outside the radial direction of the line connecting the hinge pins 24 and 28, i.e., the untriggered position. The centrifugal device is thus stably in an untriggered state, without unnecessary vibration and wear, and can maintain consistent motion over a long period of time. The intermediate member 90 is restrained by the circumferential direction of the limiting mechanism CM, and does not interfere with the guiding member 50 in both circumferential directions, and is even less likely to enter the wedge. As shown in the lower half of Fig. 2, when the rotational speed of the drive shaft 210 exceeds the set value, the centrifugal force acting on the centrifugal weight 20 will first cause the connecting rod 22 to start to rotate radially outward, and then in a very short time. The inner force of the force-limiting spring 38 is overcome and after the spring is slightly stretched, the hinge pin 26 is caused to pass over its unsteady critical point on the line connecting the hinge pins 24 and 28, instantaneously flipping over and reaching its connection. The extreme position within the radial direction is also the trigger position. The centrifugal device is thus in a stable triggering state, and the limiting groove 118 is located at the outermost position of the axial direction with the limiting ring 120, thereby releasing the circumferential constraint of the limiting mechanism CM on the intermediate member 90, so that the limiting device is obtained. The ability to enter the wedge in any circumferential direction. At this time, the link 22 abuts against the groove of the lug 32 to position the slope 36, or the outer arc surface 44 of the sector link 40 abuts against the inner end surface of the follower ring 30.

另外，触发机构 AC还最佳地包括一个螺旋促动机构。该机构的座环 77同轴线地设置在摩擦件 70的端面上，促动环 48借助较大升角的螺旋副可转动地设置在座环 77外周面上，并被一设置在其与摩擦件 70外端面之间的周向复位弹性元件（未示出），持续地弹压 /弹拉向远离径向面 42的转动方向。未触发状态中，促动环 48与扇形连杆 40的径向面 42最佳地间隙相隔。当促动环 48响应促动信号并克服所述弹性元件的阻力而相对座环 77转动时，其轴向导向移动将通过对径向面 42的 4氏触，驱动扇形连杆 40径向内转，从而致动触发机构 AC。显然，当促动信号具体为断绳信号时，感应钢丝拉绳 208 最佳地通过弹性元件周向拉动促动环 48做出促动转动。而当促动信号具体为诸如电子测量装置发出的高精度超速信号，或者诸如必需紧急制动的停电或故障断电信号时，可借助设置于促动环 48径向外侧摩擦件 70端面上的常开或常闭电磁继电机构，或者步进电机等（均未示出），通过例如钢丝绳之类的挠性件，周向拉动促动环 48 做出促动转动。当然，如果需要，也可将一个实施紧急制动的并联触发权力，交给轿厢内的乘客。例如，设置一个与钢丝拉绳 208 并联的另一根钢丝绳，并将该钢丝绳控制端的固定连接点延伸至轿厢内壁上。 In addition, the trigger mechanism AC also preferably includes a screw actuating mechanism. The seat ring 77 of the mechanism is coaxially disposed on the end surface of the friction member 70, and the actuating ring 48 is rotatably disposed on the outer peripheral surface of the seat ring 77 by means of a screw having a large angle of elevation, and is disposed in the friction ring. A circumferentially returning resilient member (not shown) between the outer end faces of the member 70 continuously urges/balls away from the direction of rotation of the radial face 42. In the untriggered state, the actuating ring 48 is optimally spaced from the radial face 42 of the sector link 40. When the actuating ring 48 rotates relative to the seat ring 77 in response to the actuation signal and against the resistance of the resilient member, its axially guided movement will drive the fan link 40 radially inwardly through the contact of the radial face 42 Turn to activate the trigger mechanism AC. Obviously, when the actuation signal is specifically a rope break signal, the induction wire drawstring 208 optimally pulls the actuating ring 48 through the resilient member to effect an actuating rotation. When the actuation signal is specifically a high-precision overspeed signal such as that emitted by the electronic measuring device, or a power failure or fault power-off signal such as an emergency braking, it may be provided on the end surface of the radially outer friction member 70 of the actuating ring 48. A normally open or normally closed electromagnetic relay mechanism, or a stepper motor or the like (none of which is shown), is urged by a circumferentially pulling actuating ring 48 by a flexure such as a wire rope. Of course, if necessary, a parallel triggering power to carry out emergency braking can also be given to the passengers in the car. For example, a further wire rope in parallel with the wire rope 208 is provided and the fixed connection point of the wire rope control end is extended to the inner wall of the car.

无疑，该螺旋促动机构不是唯一的。由公知技术和常识，可以构思出众多的可促动 /致动触发机构 AC的装置。同样，离心装置也公知地不止上迷一种。 Undoubtedly, the screw actuation mechanism is not unique. A number of devices that can actuate/actuate the triggering mechanism AC can be conceived by known techniques and common sense. Likewise, centrifugal devices are also known for more than one.

如果需要，触发机构 AC显然也可以被一个一端可转动地连接至传动轴 210，或固定连接至轴承座 204, 另一端固定连接至摩擦件 70的封装壳密封住。 If desired, the trigger mechanism AC can obviously also be rotatably coupled to the drive shaft 210 by one end, or fixedly coupled to the bearing housing 204, and the other end of the package fixedly coupled to the friction member 70 can be sealed.

紧急制动装置 B1的工作过程非常简单。正常状态中，触发机构 AC处于图 2上半部所示的未触发状态。中介件 90被撤销入楔能力，上下运行中的轿厢 200 可通过随动齿轮 110, 带动传动轴 210在两个圓周方向上相对摩擦件 70 自由地任意转动。而一旦轿厢 200超速上升或下降，传动轴 210的转速必然超过其上限设定值。于是，作用于离心配重 20的离心惯性力将克服限力弹簧 38的拉力，在极短的时间内使离心装置如上所述地产生径向翻转动作，从而致使触发机构 AC触发周向限位机构 CM, 以将后者的限位环 120轴向拉出，最终解除后者对中介件 90的周向对中式限制，从而赋予中介件 90 自由入楔的能力，也就是赋予制动机构摩擦制动的能力。无疑，利用诸如离心配重 20的径向位移，或者扇形连杆 40的外圓弧面 44的轴向移动，或者位于摩擦件 70的对应于周向凹槽 78 的外表面上的应力传感元件的应变电信号，还可触动相应信号开关，或直接发出电信号，以发出相应指令或执行相关安全操作。 The working process of the emergency brake device B1 is very simple. In the normal state, the trigger mechanism AC is in the untriggered state shown in the upper half of FIG. The interposer 90 is revoked into the wedge capability, and the car 200 in the up and down operation The drive shaft 210 can be arbitrarily freely rotated relative to the friction member 70 in two circumferential directions by the follower gear 110. Once the car 200 has risen or fallen overspeed, the speed of the drive shaft 210 must exceed its upper limit setting. Thus, the centrifugal inertial force acting on the centrifugal weight 20 will overcome the tension of the force-limiting spring 38, causing the centrifugal device to generate a radial flipping action as described above in a very short period of time, thereby causing the trigger mechanism AC to trigger the circumferential limit. The mechanism CM pulls the latter of the limiting ring 120 axially, and finally releases the circumferential centering restriction of the intermediate member 90, thereby giving the intermediate member 90 the ability to freely enter the wedge, that is, imparting friction to the brake mechanism. Braking ability. Undoubtedly, the radial displacement such as the centrifugal weight 20, or the axial movement of the outer circular arc surface 44 of the sector link 40, or the stress sensing element on the outer surface of the friction member 70 corresponding to the circumferential groove 78 is utilized. The strained electrical signal can also activate the corresponding signal switch, or directly send an electrical signal to issue a corresponding command or perform related safety operations.

于是，当导向件 50继续地沿图 4A中例如箭头 P所指方向相对摩擦件 70转动时，摩擦件 70将借助牵引摩擦机构 F1的空载 /牵引摩擦转矩，牵引着转动导向机构 G的中介件 90, 相对导向件 50沿箭头 R所指方向作转动导向运动。该转动导向运动所产生的轴向移动 /胀紧力，在将导向齿 92瞬间楔紧在导向面 54a 和牵引摩擦面 72所围成的端面楔形空间中，也就是中介件 90将导向件 50与摩擦件 70楔合成一个摩擦体，牵引摩擦机构 F1 因而轴向接合的同时，还将导向件 50即刻胀紧在摩擦件 70的另一个内端面也就是传力摩擦面 74上，以形成轴向力封闭式抵触连接的方式，致使传力摩擦机构 F2也同步接合，并将导向件 50 与摩擦件 70直接连接成一个摩擦体。 Thus, when the guide member 50 continues to rotate relative to the friction member 70 in the direction indicated by the arrow P in FIG. 4A, the friction member 70 will pull the rotary guide mechanism G by the idle/traction friction torque of the traction friction mechanism F1. The intermediate member 90 is rotated and guided in the direction indicated by the arrow R with respect to the guide member 50. The axial movement/expansion force generated by the rotational guiding motion is instantaneously wedged in the end face wedge-shaped space surrounded by the guiding surface 54a and the traction friction surface 72, that is, the intermediate member 90 will guide the member 50. The friction member 70 is wedged to form a friction body, and the traction friction mechanism F1 is thus axially engaged, and the guide member 50 is also immediately expanded on the other inner end surface of the friction member 70, that is, the force transmitting friction surface 74, to form the shaft. The force-closed contact connection means that the force-transmitting friction mechanism F2 is also synchronously engaged, and the guide member 50 and the friction member 70 are directly connected to form a friction body.

于是，紧急制动装置 B1 随着空间楔形机构的楔合而接合。由管状基体 60 内孔中的传动轴 210传入的基于轿厢 200的重力和运动惯性的驱动转矩 Mo，分成经由转动导向机构 G和牵引摩擦机构 F 1传递的楔合摩擦转矩 , 以及经由传力摩擦机构 F2直接传递的传力摩擦转矩 M₂, 分别传递给摩擦件 70, 并最终作用至不可转动的轿厢 200。其中，

Mi + Ms, 且上述轴向胀紧力、楔合力和各摩擦力的大小，均完全自适应地正比于 , 也就是驱动转矩 M₀。 Thus, the emergency brake device B1 is engaged with the wedge of the space wedge mechanism. The driving torque Mo based on the gravity and the moving inertia of the car 200, which is transmitted from the transmission shaft 210 in the inner hole of the tubular base 60, is divided into the wedge friction torque transmitted via the turning guide mechanism G and the traction friction mechanism F1, and The force-transmitting friction torque M ₂ directly transmitted via the force-transmitting friction mechanism F2 is transmitted to the friction member 70, respectively, and finally to the non-rotatable car 200. among them,

Mi + Ms, and the above-mentioned axial expansion force, the wedge force and the magnitude of each friction force are completely adaptively proportional to, that is, the driving torque M ₀ .

无疑地，由于周向上的对称性，导向件 50沿图 4中箭头 R所指方向相对摩擦件 70的转动，具有完全类似的工作过程，所以无需重复说明。 Undoubtedly, due to the symmetry in the circumferential direction, the guide member 50 has a completely similar working process with respect to the rotation of the friction member 70 in the direction indicated by the arrow R in Fig. 4, so that it is not necessary to repeat the explanation.

这里应特别说明的是，如上所述，紧急制动装置 B1仅在具有 ζ < λ < ξ的设置中，可以获得自适应地相对驱动转矩过载打滑的摩擦制动功能，但前提是转矩必需由导向件 50向摩擦件 70传递，也就是沿如上所述的路径方向传递，而不是相反。而由动量矩定理 /动量定理的运动学基本常识可知，基于轿厢 200 的重力和运动惯性的驱动转矩 Μ。是一个有限量，其不足以驱动存在相当大转动惯量的轿厢 200绕轴线 X的转速，在制动装置 B1接合制动的瞬间产生阶跃式的飞升，尤其是在轿厢 200被限制摆动，或者图 1中的左右两个制动装置 B1的传动轴 210具有互反的旋转方向之际（齿条面对相反方向设置时）。所以，具有 ζ < λ ξ设置的制动装置 Bl的上述楔合式制动接合过程，必然是一个自适应地出现短暂的过载式摩擦滑转的过渡过程，直至轿厢 200被制停在齿条 202上为止，而不会产生有害冲击。整个摩擦滑转制动过程中，楔合式制动转矩 /轴向接合力将始终自适应地等于 Z对应于驱动转矩 M_Q, 不会小于 M_Q, 更不会等于零。即，不会制动失效。从而以刚性楔合的纯机械结构，获得了自适应式 ABS防抱死的制动效果。而且自适应地具有最佳的打滑时间，该打滑时间与轿厢 200 满载或空载相关度不大，特别优于自动扶梯中的严重相关的现有技术。 It should be particularly noted here that, as described above, the emergency brake device B1 can obtain the friction braking function adaptively relative to the driving torque overload slip only in the setting with ζ < λ < ,, but the premise is the torque It must be transmitted by the guide 50 to the friction member 70, that is, in the direction of the path as described above, rather than the reverse. The basic knowledge of kinematics of the momentum moment theorem/momentum theorem can be known to be based on the driving torque of the gravity and motion inertia of the car 200. Is a finite amount that is insufficient to drive the rotational speed of the car 200 having a relatively large moment of inertia about the axis X, producing a stepped fly-up at the moment the brake device B1 engages the brake, especially when the car 200 is restrained from swinging. Or, the drive shafts 210 of the left and right brake devices B1 in FIG. 1 have reciprocal rotational directions (when the racks are disposed in opposite directions). Therefore, the above-described wedge-type brake engagement process of the brake device B1 having the ζ < λ ξ setting is necessarily a transient process of adaptively experiencing a brief overload-type frictional slip until the car 200 is stopped at the rack Up to 202, without harmful effects. During the entire friction slip braking process, the wedge braking torque/axial engagement force will always be adaptively equal to Z corresponding to the driving torque M _Q , not less than M _Q , and not equal to zero. That is, there is no brake failure. Thus, the adaptive ABS anti-lock is obtained with a purely mechanical structure with rigid wedges. Dead braking effect. Moreover, it is adaptively optimal to have a slip time that is less correlated with the full load or no load of the car 200, and is particularly superior to the severely related prior art in escalators.

另外，具有 0 < λ < ζ (针对 ζ 〉0的情况）设置的紧急制动装置 Bl , 将如上所述地具有无滑转 /动的瞬时制停特征，与现有技术中无弹性緩冲的安全钳装置一样，致使轿厢承受很大冲击。当然，只要在轴向力封闭式抵触连接的除导向摩擦副之外的路径中的同一摩擦副的两个轴向抵触面之间，加入诸如碟簧的至少一个弹性元件，即可利用转动导向机构 G的对应于该弹性元件的可压缩量的相对滑转爬升，对该制停过程予以有限程度的緩冲（相当于现有技术）。例如，将该弹性元件以间隔一个与传动轴 210 不可旋转相连的盘形圓环的方式，设置在传力摩擦面 58和 74之间，或者直接设置在图 5中的支撑端面 189与 224之间。更为详细的相关结构图示和说明，可参见全文引用于此的，由本申请人于本申请同日提出的名为空间楔合式摩擦连接器的中国专利申请。当然，还可以设置周向阻尼机构，例如，针对图 5中的中介件 90的阻尼机构，以使紧急制动装置 B2获得柔性接合的能力。 In addition, the emergency brake device B1 having 0 < λ < ζ (for the case of ζ > 0) will have the non-slip/moving instantaneous stop function as described above, and the inelastic buffer in the prior art. Like the safety clamp device, the car is subjected to a large impact. Of course, as long as at least one elastic element such as a disc spring is added between the two axial abutment faces of the same friction pair in the path of the axial force-closed contact but the guide friction pair, the rotation guide can be utilized. The relative slippage of the mechanism G corresponding to the compressible amount of the elastic element imparts a limited degree of cushioning to the stopping process (equivalent to the prior art). For example, the elastic member is disposed between the force transmitting friction faces 58 and 74 at intervals of a disc-shaped ring that is non-rotatably coupled to the drive shaft 210, or directly disposed at the support end faces 189 and 224 of FIG. between. For a more detailed description of the related art, reference is made to the Chinese Patent Application entitled Space Wedge Friction Connector, which is hereby incorporated by reference in its entirety herein. Of course, a circumferential damping mechanism, such as the damping mechanism for the interposer 90 of Figure 5, can also be provided to provide the emergency braking device B2 with the ability to flexibly engage.

紧急制停之后，如果需要解除该制停状态，只需手工或借助相应圓环将连杆 22内径向地同步按压至未触发位置即可。此时，随动座环 30将自然地轴向移离凸缘 214b, 并压缩复位弹簧 154。随后提升或降下轿厢 200, 传动轴 210将产生解楔转动，限位环 120便可在复位弹簧 154的弹力作用下，于限位凹槽 118 第一次周向对准限位凸起 68并将其收纳之际，与随动座环 30—道同步回复至其稳定的未触发位置。一般地，在不知道楔合方向的情况下，完成上述解楔转动最多只需要上下曳引轿厢 200各一次。而当转动导向机构 G具有图 4B的单向齿设置时，也就是紧急制动装置 B1只具有防坠落的制动功能时，则只需一次提升便可解楔。 After the emergency stop, if it is necessary to release the stop state, it is only necessary to manually press the link 22 radially to the untriggered position by hand or by means of the corresponding ring. At this point, the follower ring 30 will naturally move axially away from the flange 214b and compress the return spring 154. Then, the car 200 is lifted or lowered, and the drive shaft 210 will be unwrapped. The limit ring 120 can be aligned with the limit projection 68 for the first time in the limit groove 118 under the elastic force of the return spring 154. When it is stored, it will return to its stable untriggered position synchronously with the follower ring 30-way. In general, in the case where the direction of the wedging is not known, it is only necessary to drag the car 200 up and down at most once. When the rotary guide mechanism G has the one-way tooth arrangement of Fig. 4B, that is, when the emergency brake device B1 has only the anti-fall brake function, the wedge can be unwrapped with one lift.

另外，对于响应于曳引钢绳断开，其它检测机构给出的超速电信号，或者故障断电等信号而需要紧急制动的情形，可依照如上所述的方式致动促动环 48，其后的工作过程则完全同上，此处已无需重复说明之必要。 In addition, in the case where an emergency braking is required in response to the breaking of the traction wire, the overspeed electrical signal given by the other detecting mechanism, or the faulty power failure, the actuating ring 48 may be actuated as described above. The subsequent work process is exactly the same as above, and there is no need to repeat the explanation here.

另外，当紧急制动装置 B1用于例如自动扶梯的防断链和防超速制动时，只需将传动轴 210 直接用作其从动链轮的轮轴，或由其充当，或与其耦合，并将感应钢丝拉绳 208 的另一头，参照公知技术连接至感应滑靴即可。例如，参照专利文献 CN101513973A。这样，制动装置 B1既可用于驱动链条断开和过度松弛时的紧急制动，也可同时用于梯级链 /台阶链超速运行时的紧急制动，以及故障断电时的紧急制动，更可同时用于正常断电停机的工作制动。而且没有沖击，更节省一个工作制动器。当然，此时应将触发机构 AC中的开关式离心装置变型为渐变式动作机构，以省去正常起动前需要人工复原该装置的麻烦。例如，将拉簧式限力弹簧 38简单地改为设置于随动座环 30和限位环 120之间的限力压簧，或者参照公知技术的其它方案执行。这样，触发机构 AC便具有自动复位的能力，工作时直接起动即可。即便在紧急制动后，即便用于曳引电梯，也只需以点动方式提升一次梯级 /轿厢 200, 即可于解楔之际令触发机构 AC自动复位。 In addition, when the emergency brake device B1 is used for, for example, an anti-break chain and an overspeed brake of an escalator, it is only necessary to directly use the drive shaft 210 as the axle of its driven sprocket, or to act as, or be coupled thereto, The other end of the induction wire drawstring 208 can be attached to the induction shoe with reference to known techniques. For example, refer to patent document CN101513973A. In this way, the brake device B1 can be used for both emergency braking when the chain is disconnected and excessively slack, or for emergency braking when the step chain/step chain is overspeeded, and for emergency braking when the power is off. It can also be used for working brakes with normal power failure. And without impact, it saves a working brake. Of course, at this time, the switching centrifugal device in the trigger mechanism AC should be changed into a gradual action mechanism, so as to save the trouble of manually recovering the device before the normal start. For example, the tension spring type force limiting spring 38 is simply changed to a force limiting spring disposed between the follower seat ring 30 and the limit ring 120, or by other means known in the art. In this way, the trigger mechanism AC has the ability to automatically reset, and can be started directly during operation. Even after emergency braking, even if it is used to steer the elevator, it is only necessary to raise the step/car 200 in a jog mode, so that the trigger mechanism AC can be automatically reset at the time of unwinding.

有必要指出的是，紧急制动装置 B1 用于自动扶梯 /移动人行道的制动时，其自适应于负载转矩大小的楔合式制动转矩，将令其轻^ H也具有稳定的制停距离和制停时间。明显地优于制动转矩不是因满载而显得相对不足，就是因空载而显得相对过大，或者因使用永磁同步电动机而显得相对过大，因而不易满足规定的制停时间和制停距离的现有技术。 It is necessary to point out that when the emergency brake device B1 is used for the braking of the escalator/moving sidewalk, the wedge-type braking torque adaptive to the load torque will make it light and stable. Distance Departure and stop time. Obviously better than the braking torque is not relatively insufficient due to full load, it is relatively large due to no-load, or it is relatively large due to the use of permanent magnet synchronous motor, so it is difficult to meet the specified stoppage time and stop The prior art of distance.

另外，在无需双向制动，尤其是在自动扶梯的仅需单向制动的应用部位，紧急制动装置 B1中的导向齿 52和 92, 应最佳地设置成如图 4B所示的锯齿形。此时，只要以一个受方向开关控制的诸如电磁继电机构按如上所述的方式驱动促动环 48转动，也就是人为地将触发机构 AC维持在触发状态，即可简单、可靠地于逆转零时刻实现制止自动扶梯逆转的功能，且无丝毫冲击的可能。 In addition, the guide teeth 52 and 92 in the emergency brake device B1 should be optimally arranged as saw teeth as shown in Fig. 4B, without the need for two-way braking, especially in the application portion of the escalator requiring only one-way braking. shape. At this time, as long as the actuator ring 48 is driven to rotate in a manner as described above by an electromagnetic relay mechanism controlled by the direction switch, that is, the trigger mechanism AC is artificially maintained in the trigger state, the reverse can be simply and reliably reversed. At zero time, the function of stopping the escalation of the escalator is realized, and there is no possibility of any impact.

至此不难发现，紧急制动装置 B1与现有技术的安全钳装置一样，均完全经由力封闭的面接触摩擦机构传递摩擦转矩，因此显然地，依据本发明的紧急制动装置 B1具有至少不差于该现有技术的转矩能力和结构强度。但由于本发明的技术方案完全基于可循环回转的空间楔合式摩擦制动机理，并具有轴向力封闭的湿式独立封闭结构，制动时并不对外产生高温高热和火花。而且，齿轮齿条不用于动力传动，不担心一般污染，无需高精度和精维护，只要能保持啮合关系和基本强度即可。因此，本发明的应用显然无关于具体的使用环境，无论室内室外地上地下，或者是否易燃易爆场所，均具有明显的通用性，其结构强度和转矩容量也显然优于现有技术，并具有显著为高工作寿命。同时，其显然拥有更小的体积和质量。而作为一个***，其省去了体积庞大和安装调试麻烦的限速器***，提拉连杆***等等，其整个制动***集中于一处，工作参数和精度全由制造者决定，大大方便了现场安装和维护修理。因而，在大幅降低*** 复杂程度，大幅降低制作、安装调试和维护成本的同时，本发明更拥有远远为小的***体积，简单而紧凑的结构，以及显著为高的工作一致性、可靠性和安全性。 It is not difficult to find that the emergency brake device B1 transmits the friction torque completely via the force-closed surface contact friction mechanism, as is the case with the prior art safety gear device, so that the emergency brake device B1 according to the invention has at least Not worse than the torque capability and structural strength of this prior art. However, since the technical solution of the present invention is completely based on the space-wrap friction friction mechanism of the revolving rotation and the wet independent closed structure with axial force closure, high temperature and high heat and spark are not generated when braking. Moreover, the rack and pinion are not used for power transmission, and there is no fear of general pollution, and high precision and fine maintenance are not required, as long as the meshing relationship and basic strength can be maintained. Therefore, the application of the present invention obviously has no specific use environment, and has obvious versatility, whether it is underground or underground, or whether it is a flammable or explosive place, and its structural strength and torque capacity are obviously superior to the prior art. And has a significant high working life. At the same time, it clearly has a smaller size and quality. As a system, it eliminates the volume limiter system that is bulky and troublesome to install and debug, the lifting link system, etc., and the entire braking system is concentrated in one place. The working parameters and precision are all determined by the manufacturer, Convenient on-site installation and maintenance repairs. Thus, while significantly reducing system complexity and significantly reducing manufacturing, installation, commissioning, and maintenance costs, the present invention has a much smaller system size, a simpler and more compact structure, and significantly higher work consistency and reliability. And security.

对于矿用罐笼 /斜坡车厢等没有齿条的情形，可以通过设置该导轨式齿条或直接使用制动车轮等的方案，依靠例如车轮与导轨之间的摩擦力来制动车厢。 In the case of a mine cage/ramp car without a rack, it is possible to brake the car by means of friction between the wheel and the guide rail by providing the rail type rack or directly using the brake wheel or the like.

更值得指出的是，依据本发明的紧急制动装置，还具有操纵简便且易于线控的优点，以及可最方便地集中实现分別或同时基于断绳 /断链、超速、故障断电和正常停机 /停电等多种机械 /电信号中的任何一个而独立触发制动动作的优点，并因此可同时用作工作制动器。 It is more worth noting that the emergency braking device according to the present invention has the advantages of simple operation and easy wire control, and can be conveniently and conveniently realized separately or simultaneously based on broken rope/chain breaking, overspeed, fault power off and normal. The advantage of braking action is independently triggered by any of a variety of mechanical/electrical signals, such as shutdown/blackout, and can therefore be used as an operating brake at the same time.

容易明了，响应于断绳 /断链的机械拉动信号，以及响应于超速、故障停电和正常停机 /电等电信号的触发式致动，也可按不影响离心式触发机构 AC的方式，直接触发限位环 120。例如，在限位环 120与随动座环 30之间设置一个螺旋压簧，在限位环 120的径向凸耳与摩擦件 70之间空套一个盘形环，将扇形连杆 40改为铰接至该盘形环，将促动环 48改为抵触至限位环 120的径向凸耳。 It is easy to understand, in response to the mechanical pull signal of the broken rope/broken chain, and the triggering actuation in response to the overspeed, fault power failure and normal shutdown/electrical signals, it can also be directly in the way of not affecting the centrifugal trigger mechanism AC. The limit ring 120 is triggered. For example, a spiral compression spring is disposed between the limiting ring 120 and the follower ring 30, and a disc ring is disposed between the radial lug of the limiting ring 120 and the friction member 70, and the sector connecting rod 40 is changed. To articulate to the disc ring, the actuating ring 48 is modified to abut against the radial lugs of the stop ring 120.

作为本领域的技术人员不难想到，为应对慢速运行的升降设备，例如，针对以永磁电机为动力源的自动扶梯等，可借助适当设置连杆 22的长度，或者将包括离心装置的触发机构 AC设置在与传动轴 210耦合的增速装置上，再通过诸如钢绳的挠性连接件拉动促动环 48的方式，来实现紧急制动的发明目的。而如果需要，紧急制动装置 B 1显然也可固定在轿厢 200内部空间的顶面上，齿条 202 可以设置有花键齿，圓柱销齿或者销型齿等等。同样不难想到，触发机构 AC并不必需具有立体结构，其也可以具有只存在两个互反的开关式稳定工位的平面结构，例如利用文献 CN101356114A 中所述的可动配重机构 21。即，将可动配重机构设置于具有阻挡限位环 120弹性外移的卡爪的行星式座板上，利用触发后静止挡块对可动配重机构的径向触碰，转动该行星式座板，从而致其卡爪周向转动，最终解除其对限位环 120轴向阻挡。 As a person skilled in the art, it is not difficult to think that in order to cope with a slow running lifting device, for example, for an escalator using a permanent magnet motor as a power source, the length of the connecting rod 22 may be appropriately set, or a centrifugal device may be included. The triggering mechanism AC is disposed on a speed increasing device coupled to the drive shaft 210, and the purpose of the emergency braking is achieved by pulling the actuating ring 48 by a flexible connecting member such as a steel cord. If desired, the emergency brake device B1 can obviously also be fixed to the top surface of the interior space of the car 200. The rack 202 can be provided with spline teeth, cylindrical pin teeth or pin-shaped teeth and the like. It is also not conceivable that the triggering mechanism AC does not have to have a three-dimensional structure, it can also have a planar structure with only two reciprocating switching-stable stations, for example using the movable counterweight mechanism 21 described in document CN101356114A. That is, the movable weight mechanism is disposed on the planetary seat plate having the claw that blocks the elastic movement of the limit ring 120, and the planet is rotated by the radial contact of the movable weight mechanism after the triggering static stop The seat plate is such that its claw rotates circumferentially, and finally its axial blocking of the limit ring 120 is released.

由上述说明不难看出，本发明的操动机构最佳地具体为周向限位机构 CM 的目的，就是将中介件 90可靠地限定在相对导向件 50的特定的周向位置上。在该位置上，中介件 90将不可能入楔。即，中介件 90不可能进入将导向件 50 与摩擦件 70可驱动地连接 /结合 /楔合成一个摩擦体的工作过程和状态。所以，周向限位机构 CM不受形式上的限制，本发明并不要求中介件 90必需保持与导向件 50的严格对中，也不要求该机构必需直接设置在两构件或其端面之间。其限位凸起 68和限位凹槽 118，可以分别直接或间接地设置在中介件 90和导向件 50上。例如，图 2中的凹槽 118，就是间接地设置在导向件 50上。 It will be apparent from the above description that the operating mechanism of the present invention is best specifically embodied as a circumferential stop mechanism CM for reliably defining the intermediate member 90 at a particular circumferential position relative to the guide member 50. In this position, the interposer 90 will not be able to enter the wedge. That is, the interposer 90 is unlikely to enter the working process and state in which the guide member 50 and the friction member 70 are drivingly coupled/bonded/wedged into a friction body. Therefore, the circumferential limiting mechanism CM is not limited in form, and the present invention does not require the intermediate member 90 to be strictly aligned with the guiding member 50, nor is it required to be directly disposed between the two members or their end faces. . The limiting protrusion 68 and the limiting groove 118 can be directly or indirectly disposed on the intermediate member 90 and the guiding member 50, respectively. For example, the recess 118 in Fig. 2 is disposed indirectly on the guide member 50.

还应该指出的是，为谋求更大的设计自由度和使空间楔形机构更容易地楔合或解楔，本发明还具有各种提升极限角 ζ和 ξ数值的技术手段。包括，将转动导向机构 G的导向面 54和 94设置成倾斜螺旋型齿面，将牵引摩擦机构 F1的摩擦面 72和 104设置成截锥面，致使轴截面内导向面 54和 94或摩擦面 72和 104与轴线 X的夹角 /半锥顶角不等于 90度，而等于 0 - 180度的其它值；将牵引摩擦机构 F1设置成多摩擦片式结构；以及，将具备更大摩擦系数的材料或元件附装至摩擦面 72和 104中的至少一个上。例如，在静摩擦系数均为 0.10时，制动装置 B1中的 ζ和 ξ分别等于 0度和 11.4度，而只需将牵引摩擦机构 F1的摩擦面设置成半锥顶角等于 30度的截锥面这一个措施，上述极限角便分别升至 5.6度和 17.02度。这里应顺便提及的是，本说明书已经给出了关于极限角 ζ和 ξ的清晰的文字定义和说明，无需付出任何创造性的劳动，本领域的普通技术人员均可据此推导出其函数关系式 /计算公式。 It should also be noted that the present invention also has various techniques for increasing the limit angle ξ and ξ values in order to achieve greater design freedom and to make the space wedge mechanism easier to wedge or unwrap. Including, the guide faces 54 and 94 of the rotary guide mechanism G are disposed as inclined spiral tooth faces, and the friction faces 72 and 104 of the traction friction mechanism F1 are disposed as truncated cone faces, so that the guide faces 54 and 94 or the friction faces in the shaft section are formed. The angle between the 72 and 104 and the axis X/half cone apex angle is not equal to 90 degrees, and is equal to other values of 0 - 180 degrees; the traction friction mechanism F1 is set to a multi-friction disc structure; and, there will be a larger friction coefficient The material or component is attached to at least one of the friction surfaces 72 and 104. For example, when the static friction coefficient is 0.10, the ζ and ξ in the brake device B1 are equal to 0 degrees and 11.4 degrees, respectively, and only the friction surface of the traction friction mechanism F1 is set to a truncated cone with a half cone angle equal to 30 degrees. In this measure, the above limit angles are raised to 5.6 degrees and 17.02 degrees respectively. It should be mentioned here that, in this specification, a clear textual definition and description of the limit angles ξ and ξ have been given, without any creative labor, and one of ordinary skill in the art can derive the functional relationship therefrom. Formula / calculation formula.

由常识可知，为增大同等直径时紧急制动装置 B1的转矩容量并降低轴向内力，牵引摩擦机构 F1和传力摩擦机构 F2也可依公知技术，被如上所述地分别或同时设置为多摩擦片式的离合机构，并因此而具有多于一个的一组牵引摩擦副或传力摩擦副。例如，参见图 2，依照公知技术并借助设置在通孔或外周面缺口中的两组轴向销，将轴向上分别介于摩擦面 72与 104以及传力摩擦面 58与 74之间的，各至少包括一个的各一组环状外摩擦片，不可旋转地连接至牵引摩擦面 72和传力摩擦面 74, 再借助诸如花键副，将对应的各至少包括一个的各一组环状内摩擦片，以与上述外摩擦片轴向交错排列的形式，分别相应地且不可旋转地连接至位于传力摩擦面 58和回转摩擦面 104内环侧的环形端面凸缘的外周面。 It is known from common knowledge that in order to increase the torque capacity of the emergency brake device B1 at the same diameter and reduce the axial internal force, the traction friction mechanism F1 and the force-transmitting friction mechanism F2 can also be separately or simultaneously set as described above according to known techniques. It is a multi-friction disc clutch mechanism and thus has more than one set of traction friction pairs or force-transmitting friction pairs. For example, referring to Fig. 2, axially spaced between friction surfaces 72 and 104 and force transmitting friction surfaces 58 and 74, respectively, in accordance with known techniques and by means of two sets of axial pins disposed in the through holes or outer peripheral notches. Each of the plurality of annular outer friction plates each including at least one is non-rotatably coupled to the traction friction surface 72 and the force transmitting friction surface 74, and the corresponding ones each include at least one set of rings by means of, for example, a spline pair The inner friction plates are respectively correspondingly and non-rotatably connected to the outer circumferential surfaces of the annular end face flanges on the inner ring side of the force transmitting friction surface 58 and the rotary friction surface 104 in a manner of being axially staggered with the outer friction plates.

容易想到，如果在传力摩擦面 58和 74之间再轴向对称地设置一个中介件 90，并与导向件 50及摩擦件 70分别对称地组成再一个转动导向机构 G和牵引摩擦机构 F1 , 制动装置 B1将失去传力摩擦机构 F2而具有两个共用同一个摩擦件 70的牵引摩擦机构 Fl。此时，分别抵触至两个中介件 90的弹性元件 150, 应最佳地具有致使该二构件周向同步联动的功能。需要说明的是，如定义中所述，本发明没有对转动导向机构 G及其导向齿 52、 92作出具体限制，其不必需具有最佳的螺旋齿结构。因此，该机构 G及其导向齿可具有任意具备转动导向功能的形式和形状。导向齿可按离散形式设置在端面 /周面上，也可按诸如单头或多头螺纹的形式，周向延续地设置在相应的内 /外周面上。而在后一种设置形式中，其可最佳地设置成具有诸如矩形、梯形、锯齿形或三角形等截面形状的螺旋齿。同样道理，只要能够最佳地实现轴向的互补式贴合 /抵触，牵引摩擦机构 F1和传力摩擦机构 F2的各自两组回转摩擦副的截锥式回转型摩擦面，可以基于任意曲线 /母线回转而成，并可以是设置有用以散热或排除液体 /气体的沟槽的非连续表面。更多和更详细的相关图示和说明，可参见上文所整体结合的两项专利申请，此处不作进一步说明。 It is easy to think that if an intermediate member 90 is disposed axially symmetrically between the force transmitting friction surfaces 58 and 74, and the guide member 50 and the friction member 70 respectively constitute a further rotation guiding mechanism G and the traction friction mechanism F1, The brake device B1 will lose the force-transmitting friction mechanism F2 and have two traction friction mechanisms F1 sharing the same friction member 70. At this time, the elastic members 150 that respectively interfere with the two intermediate members 90 should preferably have a function of causing the two members to be synchronously synchronized in the circumferential direction. It should be noted that, as described in the definition, the present invention does not specifically limit the rotary guide mechanism G and its guide teeth 52, 92, and it is not necessary to have an optimum helical tooth structure. Therefore, the mechanism G and its guide teeth can have any form and shape with a rotational guiding function. The guide teeth may be disposed on the end face/circumferential surface in a discrete form, or may be circumferentially continuously provided on the respective inner/outer peripheral faces in the form of, for example, a single-head or multi-start thread. In the latter arrangement, however, it can be optimally arranged to have helical teeth having a sectional shape such as a rectangle, a trapezoid, a zigzag or a triangle. By the same token, as long as the axial complementary fit/resistance can be optimally achieved, the truncated cone type friction surfaces of the respective two sets of rotary friction pairs of the traction friction mechanism F1 and the force transmitting friction mechanism F2 can be based on an arbitrary curve/ The busbar is turned and can be a discontinuous surface that is provided with a groove for dissipating heat or removing liquid/gas. For more details and more detailed descriptions and illustrations, reference is made to the two patent applications incorporated by reference in its entirety herein.

实施例二：无级支撑式紧急制动装置 B2 Embodiment 2: Stepless support emergency brake device B2

如图 5 ~ 6所示，紧急制动装置 B2是对紧急制动装置 B1的改进变型。其中，未示出随动齿轮 110和轴承座 204等。 As shown in Figures 5-6, the emergency brake device B2 is an improved variant of the emergency brake device B1. Among them, the follower gear 110, the bearing housing 204, and the like are not shown.

首先，紧急制动装置 B2是包括两个转动导向机构的并联式空间楔形机构。其中，具有 0 < λ ζ设置的转动导向机构 Ga的导向齿 92a和 52a, 分别设置在中介件 90的内环侧和导向件 50a上。具有 ζ < λ < ξ设置的转动导向机构 Gb 的导向齿 92b和 52b，分别设置在中介件 90的外环侧和导向件 50b上。导向件 50b的位于导向齿 52b径向内侧的环形区域，设置有端面型周向凹槽。活动地收容在该周向凹槽中的导向件 50a, 最佳地通过花键连接方式，不可旋转地连接在该凹槽的外周面上，从而与导向件 50b 形成周向一体。同时，具体为碟形弹簧的至少一个弹性元件 100 以预压紧的形式，设置在导向件 50a和该周向凹槽的壁面之间。导向件 50a被一个设置在其与中介件 90之间的管状基体 60外周面上的卡环 184轴向限定住。 First, the emergency brake device B2 is a parallel space wedge mechanism including two rotary guide mechanisms. Among them, the guide teeth 92a and 52a of the rotary guide mechanism Ga having 0 < λ ζ are disposed on the inner ring side of the intermediate member 90 and the guide member 50a, respectively. The guide teeth 92b and 52b of the rotary guide mechanism Gb having the ζ < λ < ξ are disposed on the outer ring side of the intermediate member 90 and the guide member 50b, respectively. The annular portion of the guide member 50b located radially inward of the guide teeth 52b is provided with an end face type circumferential groove. The guide member 50a, which is movably accommodated in the circumferential groove, is preferably non-rotatably coupled to the outer peripheral surface of the groove by a spline connection so as to be circumferentially integrated with the guide member 50b. At the same time, at least one elastic member 100, specifically a disc spring, is disposed in a pre-compacted manner between the guide member 50a and the wall surface of the circumferential groove. The guide member 50a is axially defined by a snap ring 184 provided on the outer peripheral surface of the tubular base 60 between the intermediate member 90 and the intermediate member 90.

相应地，周向限位机构 CM的对中式限位凸起 68，变型为丝状的直线弹簧，其内径端贯穿性地设置在位于管状基体 60的径向通孔中，其外径端最佳地固定在中介件 90内周面的径向孔型对中式限位凹槽 118中。该两个径向孔的相邻部分最佳地呈截锥形，以允许中介件 90相对导向件 50作有限的周向和轴向弹性位移，并具有这样的设置效果。即，无外力作用之际，限位凸起 68可致使中介件 90与导向件 50a、 50b双方轴向间距持续地弹性收缩至最小，并最佳致使转动导向机构 Ga和 Gb的对应于两个圓周方向的周向间隙，均分别等于零和大于零。且在过载时，当导向齿 52b与 92b双方周向上开始相互抵触之际，对应于导向齿 52a与 92a的转动导向作用的轴向压缩，并未致使导向件 50a和 50b相互间在轴向上开始间接的刚性抵触。 Correspondingly, the centering limiting protrusion 68 of the circumferential limiting mechanism CM is modified into a wire-shaped linear spring whose inner diameter end is disposed in a penetrating manner in the radial through hole of the tubular base 60, and the outer diameter end thereof is the most Preferably, it is fixed in the radial hole type centering type limiting groove 118 of the inner circumferential surface of the intermediate member 90. Adjacent portions of the two radial bores are preferably frustoconical to allow for limited circumferential and axial elastic displacement of the interposer 90 relative to the guide member 50, and have such a setting effect. That is, when there is no external force, the limiting protrusion 68 can cause the axial distance between the intermediate member 90 and the guiding members 50a, 50b to be continuously elastically contracted to the minimum, and optimally causes the two of the rotating guiding mechanisms Ga and Gb to correspond to The circumferential clearance in the circumferential direction is equal to zero and greater than zero, respectively. And in the case of an overload, when the guide teeth 52b and 92b start to interfere with each other in the circumferential direction, the axial compression corresponding to the rotational guiding action of the guide teeth 52a and 92a does not cause the guide members 50a and 50b to be axially opposed to each other. Indirect rigid resistance begins.

于是，紧急制动装置 B2被强制楔合过程初期的摩擦转矩，具有对应于碟形弹簧弹性力的线性上升的特点。并且，对应于转动导向机构 Ga的具有弹性楔合力的空间楔形机构，同时还发挥着导引和保障对应于转动导向机构 Gb的具有刚性楔合力的空间楔形机构绝对楔合的作用。 Thus, the emergency braking device B2 is subjected to the frictional torque at the initial stage of the forced wedge process, and has a linear rise corresponding to the elastic force of the disk spring. Further, the space wedge mechanism having the elastic wedging force corresponding to the rotation guide mechanism Ga functions to guide and secure the absolute wedge of the space wedge mechanism having the rigid wedge force corresponding to the rotation guide mechanism Gb.

其次，摩擦件被设置成力封闭的组合式袋形构件，由摩擦件 70和作为袋形构件的限力元件 180不可旋转地相连而成。其中，限力元件 180与图 2中的摩擦件具有完全相同的构造。为与限力元件 180 不可旋转地相连，大致呈环状的摩擦件 70的外周面上，设置有以互补的方式沿入口 82最佳地径向延伸至开口面 88的凸缘式力臂 75。其两个径向侧表面，即是可与入口 82的两个径向侧表面同时互补式地啮合，并传递转矩的传力特征曲面。 Secondly, the friction member is provided as a force-closed combined bag-shaped member which is formed by the friction member 70 and the force-limiting member 180 as a bag-shaped member being non-rotatably connected. Wherein, the force limiting element 180 has exactly the same configuration as the friction member of FIG. 2. Non-rotatably connected to the force limiting element 180, generally annular The outer peripheral surface of the friction member 70 is provided with a flanged force arm 75 that extends optimally radially along the inlet 82 to the opening face 88 in a complementary manner. Its two radial side surfaces, that is, a force transmitting characteristic surface that can be simultaneously and positively engaged with the two radial side surfaces of the inlet 82, and transmit torque.

容易理解，也可将中介件 90与摩擦件 70合并成一个零件，将不可旋转地连接至导向件 50的传动轴 210, 变型为不可旋转地连接至增设在传力摩擦面 58 与 74之间的盘形圓环的内周面。这样，该变型中的单一导向件将作为被支撑件而与限力元件 180构成组合式袋形导向件，而摩擦件将由盘状圆环充当。 It will be readily understood that the intermediate member 90 and the friction member 70 can also be combined into a single piece that will be non-rotatably coupled to the drive shaft 210 of the guide member 50, modified to be non-rotatably coupled to the additional force transmitting friction surfaces 58 and 74. The inner circumference of the disc ring. Thus, the single guide member in this variation will constitute a combined pocket-shaped guide member with the force-limiting member 180 as a supported member, and the friction member will be acted upon by the disk-shaped ring.

第三，操动机构包括一个转动导向式无级支撑机构 SS，用以强制建立或撤销双向摩擦 /制动机构的轴向力封闭式抵触连接。该机构 SS包括作为被支撑件的摩擦件 70、支撑件 220以及限力元件 180, 参见图 5。大致呈环状的支撑件 220, 以轴向上可同时刚性抵触至摩擦件 70和盘形端部 188b的内端面也就是支撑端面 189，以及可作有限转动的方式，设置在摩擦件 70与限力元件 180之间。 Third, the operating mechanism includes a rotary-guided stepless support mechanism SS for forcibly establishing or disengaging the axial force-closed interference connection of the two-way friction/brake mechanism. The mechanism SS includes a friction member 70 as a supported member, a support member 220, and a force limiting member 180, see Fig. 5. The substantially annular support member 220 is axially rigidly engageable against the inner end surface of the friction member 70 and the disc-shaped end portion 188b, that is, the support end surface 189, and can be disposed in a limited rotation manner, and is disposed on the friction member 70 and Between the force limiting elements 180.

实际上，无级支撑机构 SS是一个以支撑件 220为中介件且具有极限角 ξ ' 的又一个空间楔形机构，其最佳地设置有类似图 4Β 所示的单向转动导向机构 UG。该导向机构 UG的两组具有互补式构造的单向螺旋型导向齿 62和 232, 分别设置在摩擦件 70和支撑件 220的相互面对的圓环形端面上，以使两者转动导向地相连接。无疑，导向齿 62和 232也可分别设置在支撑端面 224和 189上。参见图 4B, 导向齿 62和 232最佳地呈锯齿状齿形，二者设置有升角 λ ' < ξ '的螺旋导向面，最佳地平行于轴线 X的非导向面。其中， ξ '的定义同于 ξ 。 In fact, the stepless support mechanism SS is a further space wedge mechanism having the support member 220 as an intermediate member and having a limit angle ξ ', which is optimally provided with a one-way rotation guide mechanism UG similar to that shown in Fig. 4A. Two sets of the guide mechanism UG have unidirectional helical guide teeth 62 and 232 of complementary configuration, which are respectively disposed on the mutually facing annular end faces of the friction member 70 and the support member 220, so that the two are rotated and guided to the ground phase. connection. Undoubtedly, the guide teeth 62 and 232 can also be disposed on the support end faces 224 and 189, respectively. Referring to Fig. 4B, the guide teeth 62 and 232 are preferably serrated, both of which are provided with a helical guide surface having an angle of elevation λ ' < ξ ', preferably parallel to the non-guide surface of the axis X. Among them, ξ ' has the same definition as ξ.

为保证摩擦件 70、支撑件 220与限力元件 180的同轴度，支撑件 220的内径侧还设置有向两端延伸的环形端面凸缘 226, 分别可转动地连接至摩擦件 70 的阶梯内周面，以及位于限力元件 180的盘形端部 188b的阶梯内周面 84b。 In order to ensure the coaxiality of the friction member 70, the support member 220 and the force-limiting member 180, the inner diameter side of the support member 220 is further provided with an annular end face flange 226 extending to both ends, and rotatably connected to the step of the friction member 70, respectively. The inner peripheral surface, and the step inner peripheral surface 84b of the disk-shaped end portion 188b of the force-limiting member 180.

另外，支撑件 220的外周面上最佳地设置有大致沿入口 82径向延伸的扭转力臂 222。参见图 6, 该力臂 222具有适当向内倾斜的侧表面 228, 以使该力臂 222与入口 82两侧面最佳地具有转动间隙，从而保证支撑件 220相对摩擦件 70 具有足够的周向自由度 ε '。这样，在一个圓周方向上相对限力元件 180转动支撑件 220，便可在该周向自由度 ε '之内，以相互抵触的回转型支撑端面 224和 189为基准面，轴向无级地驱离 /移动摩擦件 70, 以将摩擦件 70、中介件 90和导向件 50，无间隙地刚性压紧 /抵触在传力摩擦面 74上，或者撤销该刚性压紧 / 抵触状态，从而不受阻碍和强制性地建立或撤销双向摩擦 /制动机构的轴向力封闭式抵触连接，并迫使空间楔形机构在两个圓周方向上可靠地入楔或解楔。 Further, the outer peripheral surface of the support member 220 is preferably provided with a torsion arm 222 extending substantially in the radial direction of the inlet 82. Referring to Figure 6, the force arm 222 has a lateral surface 228 that is suitably angled inwardly so that the force arms 222 and the sides of the inlet 82 optimally have a rotational clearance to ensure that the support member 220 has sufficient circumferential direction relative to the friction member 70. Degree of freedom ε '. In this way, the support member 220 is rotated relative to the force limiting member 180 in a circumferential direction, and the mutually opposite rotary support end faces 224 and 189 are used as the reference plane within the circumferential freedom ε ', and the axial direction is steplessly The friction member 70 is driven away/moved to rigidly press/impact the friction member 70, the intermediate member 90 and the guide member 50 without any gap on the force transmitting friction surface 74, or to cancel the rigid pressing/interference state, without The axial force-closed abutment connection of the two-way friction/brake mechanism is obstructed and forcibly established and revoked, and the space wedge mechanism is forced to wedge or unwrap in both circumferential directions.

其中，导向件 50和中介件 90的组合、摩擦件 70、支撑件 220三者在周向凹槽 78中的轴向自由度 δ '大于零，但小于等于上述周向自由度 ε '所对应的转动导向运动的轴向移动距离 ε ' X tg λ '。优选地，可在例如传力摩擦面 74与摩擦件 70之间设置螺旋压簧，或者，在限力元件 180的相应径向孔中设置直线钢丝弹簧，分别由牵引摩擦面 72—端作用于摩擦件 70的外径向凸缘上，以使非制动分离状态中的轴向自由度 δ '，位于摩擦机构 F1或 F2的摩擦面之间。或者，如图 5所示，设置一收缩式螺旋拉簧 152, 其两个端头分别嵌入位于摩擦件 70内周面，以及位于盘形端部 188b的内周面 84b上的径向孔中。 Wherein, the combination of the guiding member 50 and the intermediate member 90, the friction member 70, and the support member 220 have an axial freedom δ ' in the circumferential groove 78 greater than zero, but less than or equal to the rotation corresponding to the circumferential freedom ε ' The axial movement distance of the guiding motion is ε ' X tg λ '. Preferably, a helical compression spring may be disposed between, for example, the force transmitting friction surface 74 and the friction member 70, or a linear wire spring may be disposed in the corresponding radial hole of the force limiting member 180, respectively acting on the traction friction surface 72-end The outer radial flange of the friction member 70 is such that the axial freedom δ ' in the non-braking disengaged state is located between the friction surfaces of the friction mechanism F1 or F2. Alternatively, as shown in Fig. 5, a contraction coil spring 152 is provided, the two ends of which are respectively fitted in the inner circumferential surface of the friction member 70, and in the radial holes on the inner circumferential surface 84b of the disk-shaped end portion 188b. .

第四，无级支撑机构 SS还最佳地具有为其提供支撑转矩的驱动机构。该机构主要包括一个设置在转动导向机构 UG外周面上的螺旋拉簧式蓄能弹簧 156, 其两个环状端头分别套接在位于力臂 75和 222两者相对端面上的两个凸销上，以将两相邻导向齿 62和 232双方的导向面向相互贴紧的方向持续地弹拉。 Fourth, the stepless support mechanism SS also optimally has a drive mechanism for providing a supporting torque thereto. The machine The structure mainly comprises a coil spring-loaded spring 156 disposed on the outer peripheral surface of the rotating guide mechanism UG, and the two annular ends are respectively sleeved on the two protruding pins on opposite end faces of the force arms 75 and 222 Upper, the guide faces of both adjacent guide teeth 62 and 232 are continuously pulled in a direction in which they are in close contact with each other.

第五，制动装置 B2还包括一个受触发机构 AC控制的闩锁机构 BL, 用以允许无级支撑机构 SS进入支撑工况。该闩锁机构 BL主要包括控制用行星组合轮和触发件 130。其中 ,行星组合轮的行星轴 160,可转动地设置在盘形端部 188b 的位于力臂 222径向外的轴向通孔中，固结于其内端的联动齿轮 162与位于力臂 222外周面的部分轮齿 168啮合，固结于其外端的板状摆臂式锁止件 164的外径端，被触发件 130的径向延伸的钩状卡爪 132钩住 /卡合。该触发件 130借助轴销 142可转动地铰接在盘形端部 188b的外端面上。 Fifth, the brake device B2 further includes a latch mechanism BL controlled by the trigger mechanism AC to allow the stepless support mechanism SS to enter the support condition. The latch mechanism BL mainly includes a planetary combination wheel for control and a trigger member 130. The planetary shaft 160 of the planetary combination wheel is rotatably disposed in an axial through hole of the disk end 188b located radially outward of the force arm 222, and the interlocking gear 162 fixed at the inner end thereof is located at the outer periphery of the force arm 222. The partial teeth 168 of the face engage, and the outer end of the plate-like swing arm lock 164 fixed to the outer end thereof is hooked/engaged by the radially extending hook fingers 132 of the trigger member 130. The trigger member 130 is rotatably hinged to the outer end surface of the disc-shaped end portion 188b by a pivot pin 142.

当闩锁机构 BL进入闭锁工况时，锁止件 164将被触发件 130限制转动，静止的联动齿轮 162通过与轮齿的 168啮合，可将无级支撑机构 SS稳定地维持在蓄能的非支撑状态中，如图 5上半部和图 6所示。当闩锁机构 BL进入解锁工况时，锁止件 164便立即恢复自由，支撑件 220将在蓄能弹簧 156的周向拉力作用下，相对限力元件 180也就是相对摩擦件 70快速转动，例如按顺时针方向。在转动导向机构 UG的作用下，摩擦件 70将即刻被导出 δ '的距离并抵触至中介件 90 , 从而建立起双向摩擦 /制动机构的轴向力封闭式抵触连接，强制性地迫使空间楔形机构在任意圓周方向上可靠地入楔，并进而致动紧急制动装置 Β2, 如图 5下半部所示。同时，随动中的联动齿轮 162将致使锁止件 164转至如图 6 中双点画线所示的位置，例如按逆时针方向。触发件 130将自由地处于限位销 144和 146所限定的区间内，不会引发有害碰撞。紧急制动之后，只需旋转锁止件 164克服蓄能弹簧 156的反力至被触发件 130再次钩住 /卡合，即可将紧急制动装置 Β2恢复至非制动状态。 When the latch mechanism BL enters the latching condition, the lock member 164 will be restricted in rotation by the trigger member 130, and the stationary link gear 162 can stably maintain the stepless support mechanism SS in the energy storage by engaging with the gear teeth 168. In the unsupported state, as shown in the upper half of Fig. 5 and Fig. 6. When the latching mechanism BL enters the unlocking condition, the locking member 164 immediately returns to freedom, and the supporting member 220 will rapidly rotate relative to the force limiting member 180, that is, the opposing friction member 70, under the circumferential pulling force of the accumulator spring 156. For example, in a clockwise direction. Under the action of the rotation guiding mechanism UG, the friction member 70 will be immediately derived by the distance of δ ' and interfere with the intermediate member 90, thereby establishing an axial force closed contact connection of the two-way friction/braking mechanism, forcibly forcing the space. The wedge mechanism reliably wedges in any circumferential direction and in turn activates the emergency brake device 2, as shown in the lower half of Figure 5. At the same time, the follower linkage gear 162 will cause the locking member 164 to turn to the position shown by the double-dotted line in Fig. 6, for example, in a counterclockwise direction. The trigger member 130 will be freely within the interval defined by the limit pins 144 and 146 without causing a harmful collision. After the emergency braking, the emergency brake device Β2 can be restored to the non-braking state by simply rotating the lock member 164 against the reaction force of the accumulator spring 156 until the trigger member 130 is again hooked/engaged.

继续参见图 6。触发件 130最佳地是一个 "丄" 形的构件，或者 L字母形构件。其触发爪 136用于并联地接受来自诸如超速、断绳 /链、故障停电和正常停机 /电的电信号 /机械信号，并可如第一实施例中所述地产生所需的触发动作。显然，响应于这些信号的动作，应该是内径向地刚性触动触发爪 136。而来自离心装置的机械超速信号，则通过超速时离心配重 20对触发爪 134内径侧的弧形凸起 138的触碰完成。无疑，对触发爪 134和 136的触碰，均可导致触发件 130 顺时针地转动，并解除其钩状卡爪 132对锁止件 164的円锁式周向阻挡。 Continue to see Figure 6. The trigger member 130 is preferably a "丄" shaped member, or an L letter shaped member. Its triggering pawl 136 is used to accept electrical signals/mechanical signals from, for example, overspeed, broken rope/chain, fault blackout, and normal shutdown/electrical power in parallel, and can generate the desired triggering action as described in the first embodiment. Obviously, in response to the action of these signals, the triggering pawl 136 should be rigidly actuated radially inwardly. The mechanical overspeed signal from the centrifugal device is completed by the centrifugal weight 20 on the inner side of the trigger claw 134 by the centrifugal weight 20 at the time of overspeed. Undoubtedly, the touch of the triggering claws 134 and 136 can cause the triggering member 130 to rotate clockwise and release the shackle-type circumferential blocking of the locking member 164 by the hook-shaped claws 132.

应该指出的是，为了作图和说明的方便，图 5中的闩锁机构 BL被画至轴向剖面上，且图 6 中的离心装置具有最简结构。该装置的块状或球状的离心配重 20, 通过限力弹簧 38直接连接在随动座环 30的外周面上，后者则通过 D字形非圓配合的形式，固定连接至传动轴 210的位于盘形端部 188b外的最小端。当然，为提高离心装置的动作一致性和可靠性，应该参照公知技术，将其最佳地设置成只存在两个互反的开关式稳定工况的平面装置，如参照文献 CN101356114A中所述的可动配重机构 21。 It should be noted that the latch mechanism BL of Fig. 5 is drawn to the axial section for the convenience of drawing and explanation, and the centrifugal device of Fig. 6 has the simplest structure. The block or spherical centrifugal weight 20 of the device is directly connected to the outer peripheral surface of the follower ring 30 by a force limiting spring 38, and the latter is fixedly coupled to the drive shaft 210 by a D-shaped non-circular fit. Located at the smallest end outside the disc shaped end 188b. Of course, in order to improve the consistency and reliability of the operation of the centrifugal device, it should be optimally set to a planar device in which only two reciprocating switching-type stable conditions exist, as described in the reference CN101356114A. The movable weight mechanism 21 is provided.

必须指出的是，参照前文所述，无级支撑机构 SS的导向升角 λ '越接近其极限角 ξ ', 单独驱动支撑件 220作分离解楔转动的转矩就越接近于零，理论上，该转矩随着 λ '等于 ξ '而等于零。对应地，为提高无级支撑机构 SS 楔合的可靠性，此情况中蓄能弹簧 156提供的弹性力应最佳地达到相对最大。显然，通过旋转锁止件 164来驱动支撑件 220回到蓄能位置的非支撑状态的转动，应最佳地借助弹性力，并在提升或降下例如轿厢 200的过程中，随着中介件 90第一次的解楔而完成。而如果转动导向机构 G是单向机构，则无需借助弹性力，解楔即可。 It must be pointed out that, as mentioned above, the closer the guide angle λ ' of the stepless support mechanism SS is to its limit angle ξ ', the closer the torque of the separate drive support 220 to the split wedge is closer to zero, in theory , the torque is equal to zero as λ ' is equal to ξ '. Correspondingly, in order to improve the reliability of the SS of the stepless support mechanism Sexuality, in this case the spring force provided by the energy storage spring 156 should be optimally maximized. Obviously, the rotation of the unsupported state of the support member 220 by the rotary lock member 164 to return to the energy storage position should be optimally utilized by the elastic force and during the lifting or lowering of, for example, the car 200, with the interposer The first 90 wedges were completed. On the other hand, if the turning guide mechanism G is a one-way mechanism, it is not necessary to use an elastic force to unwrap the wedge.

实施例三：强制止转式紧急制动装置 B3 Embodiment 3: Forced anti-rotation emergency brake device B3

参见图 7, 紧急制动装置 B3是对紧急制动装置 B1的简单变型。其中，未示出随动齿轮 110和轴承座 204等。 Referring to Figure 7, the emergency brake device B3 is a simple variant of the emergency brake device B1. Among them, the follower gear 110, the bearing housing 204, and the like are not shown.

一方面，操动机构包括一个摩擦式止转机构 ST，用以强制地建立或撤销对中介件 90的摩擦式止转，并迫使其入楔。该止转机构 ST主要包括，设置在中介件 90外周面的截锥面 106,以及设置在入口 82中的至少包括一个的一组具有止转面的摩擦式止转件 170。该止转件 170设置有可与截锥面 106至少建立线接触摩擦副的外表面，例如，外截锥面或可互补的部分内截锥面，其通过例如 D 字形非圓配合的形式，固定连接在阶梯状销轴 172的中部周面上。销轴 172可滑动地设置在位于入口 82两端的摩擦件 70的轴向孔 81中。套设在销轴 172上的压簧式蓄能弹簧 156，以传力摩擦面 74为支撑面，将止转件 170持续地弹压向截锥面 106。由传力摩擦面 74—端延伸至摩擦件 70外端面的销轴 172的端部，固结有具有止转缺口 176的锁止件 174, 例如，借助方形孔非圓配合和卡环。该止转缺口 176, 可沿设置在摩擦件 70相应端面上的止转销 178滑动。 In one aspect, the operating mechanism includes a frictional anti-rotation mechanism ST for forcibly establishing or retracting the frictional stop of the interposer 90 and forcing it into the wedge. The rotation preventing mechanism ST mainly includes a frustoconical surface 106 provided on the outer circumferential surface of the intermediate member 90, and a set of friction type rotation preventing members 170 having a rotation preventing surface provided in the inlet 82. The anti-rotation member 170 is provided with an outer surface that can establish at least a line contact friction pair with the truncated cone surface 106, for example, an outer truncated cone surface or a complementary partial inner truncated cone surface, for example, in the form of a D-shaped non-circular fit. It is fixedly coupled to the central peripheral surface of the stepped pin 172. The pin 172 is slidably disposed in the axial bore 81 of the friction member 70 at both ends of the inlet 82. The compression spring type energy storage spring 156 is disposed on the pin shaft 172, and the force transmitting friction surface 74 is used as a supporting surface, and the rotation preventing member 170 is continuously biased toward the truncated cone surface 106. An end portion of the pin shaft 172 extending from the force transmitting friction surface 74 to the outer end surface of the friction member 70 is fixed with a locking member 174 having a rotation preventing notch 176, for example, a non-circular fitting and a snap ring by means of a square hole. The anti-rotation notch 176 is slidable along the anti-rotation pin 178 provided on the corresponding end surface of the friction member 70.

实际上，只要将止转件 170设置成中部具有所述止转面的非圓截面式阶梯轴，例如中部具有截锥面的阶梯方轴，并设置用作锁止件 174 的钩状尾部，再将蓄能弹簧 156的一端头嵌入位于其中部的相应径向孔中，止转机构 ST将具有两构件的最简结构。优选地，截锥面 106 的锥度应最佳地保证其与止转件 170 间可摩擦自锁。 Actually, as long as the rotation preventing member 170 is provided as a non-circular sectional stepped shaft having the rotation preventing surface in the middle, for example, a stepped square shaft having a truncated cone surface in the middle, and a hook-shaped tail portion serving as the locking member 174 is provided, The end of the accumulator spring 156 is then inserted into a corresponding radial bore in the middle thereof, and the anti-rotation mechanism ST will have the simplest configuration of the two members. Preferably, the taper of the truncated cone 106 is optimally ensured to be frictionally self-locking with the anti-rotation member 170.

再一方面，制动装置 B3还包括一个受触发机构 AC控制的闩锁机构 BL。该闩锁机构 BL包括锁止件 174和触发件 130。其中，锁止件 174的面对轴线 X 的一侧，最佳地设置有径向凸起。铰接在摩擦件 70外端面的位于该凸起内径侧部位的触发件 130, 具有如图 6所示的结构。其卡爪 132可设置在该凸起与摩擦件 70的外端面之间，以卡合方式阻止锁止件 174移向摩擦件 70。 In still another aspect, the brake device B3 further includes a latch mechanism BL controlled by the trigger mechanism AC. The latch mechanism BL includes a lock member 174 and a trigger member 130. Wherein, the side of the locking member 174 facing the axis X is optimally provided with a radial projection. The trigger member 130 hinged on the outer end surface of the friction member 70 at the inner diameter side of the projection has a structure as shown in FIG. The claw 132 may be disposed between the protrusion and the outer end surface of the friction member 70 to prevent the locking member 174 from moving toward the friction member 70 in a snapping manner.

设置上，上述机构具有这样的效果。即，卡爪 132轴向阻挡锁止件 174之际，也就是闩锁机构 BL进入锁 '闭工况时，止转件 170不能抵触至截锥面 106。而当卡爪 132周向移开至未轴向阻挡锁止件 174的所述径向凸起之际，也就是闩锁机构 BL进入解锁工况时，止转件 170在蓄能弹簧 156的作用下，可以抵触至截锥面 106, 在摩擦止转中介件 90的同时，还和转动导向机构 G—道，驱使其轴向抵触至牵引摩擦面 72, 并迫使其因此入楔。 In terms of settings, the above mechanism has such an effect. That is, when the claw 132 axially blocks the lock member 174, that is, when the latch mechanism BL enters the lock 'closed condition, the rotation stop member 170 cannot interfere with the truncated cone surface 106. When the claw 132 is circumferentially moved to the radial projection of the axial blocking lock member 174, that is, when the latch mechanism BL enters the unlocking condition, the rotation stop 170 is at the energy storage spring 156. Under the action, it can be in contact with the truncated cone surface 106. While frictionally stopping the interposing member 90, it is also driven to rotate the guiding mechanism G-way to axially abut against the traction friction surface 72 and force it to enter the wedge.

另外，周向限位机构 CM和触发机构 AC的结构均相同于实施例二。 In addition, the configurations of the circumferential limiting mechanism CM and the triggering mechanism AC are the same as in the second embodiment.

不难理解，摩擦式止转机构 ST也可以是一个径向止转销机构。其至少包括一个的一组销状止转件 170, 可滑动地设置在如图 7所示的径向孔 71 中，可受控地克服弹性阻力内径向地抵触至中介件 90的外周面。驱动其内径向移动的，可以是一个具有内截锥面的管状圓环。实施例四：外壳回转式紧急制动装置 B4 It is not difficult to understand that the friction type rotation stop mechanism ST can also be a radial rotation stop mechanism. It includes at least one set of pin-shaped rotation stoppers 170 slidably disposed in the radial holes 71 as shown in FIG. 7, and is controllably opposed to the outer peripheral surface of the intermediate member 90 radially against the elastic resistance. Driving the radial movement therein may be a tubular ring having an inner truncated cone. Embodiment 4: Shell rotary emergency brake device B4

参见图 8, 紧急制动装置 B4也是对紧急制动装置 B1的简单变型，并具有最简结构和轴一轴传动形式。其中，未示出随动齿轮 110, 轴承座 204, 以及触发机构 AC中的如图 2所示的离心装置。 Referring to Figure 8, the emergency brake B4 is also a simple variant of the emergency brake B1 and has the simplest construction and shaft-shaft transmission. Among them, the follower gear 110, the bearing housing 204, and the centrifugal device shown in Fig. 2 in the trigger mechanism AC are not shown.

首先，导向件 50变型为一个具有轴向力封闭功能的环状袋形构件，其实质上是将导向齿 52, 直接形成在如图 3、 6所示的袋形构件式限力元件 180的盘形环状周向凹槽 78的一个内端面上，例如盘形端部 188a的内端面上，并使限力元件 180具有圓柱形外周面的结果。相应地，周向限位机构 CM的限位环 120 可滑动地设置在其外周面上，并借助位于该外周面上的基准凸起 122, 以及位于限位环 120内周面的轴向延伸的基准槽 126, 与其不可旋转地相连。优选地，对中凹槽 118与基准槽 126连成轴向一体。对中凸起 68设置在中介件 90的力臂 95的外周面上。除了没有轮齿 168之外，该力臂 95最佳地具有相同于力臂 222 的结构。至少为一个的螺旋压簧式弹性元件 150，设置在位于导向齿 92齿底面的凹槽中，并轴向弹性 ·ί氏触至导向齿 52的齿顶面。 First, the guide member 50 is modified into an annular bag-shaped member having an axial force sealing function, which substantially forms the guide teeth 52 directly formed on the bag-shaped member type force limiting member 180 as shown in FIGS. The inner end surface of the disc-shaped annular circumferential groove 78, for example, the inner end surface of the disc-shaped end portion 188a, and the force-limiting member 180 has a cylindrical outer peripheral surface. Correspondingly, the limiting ring 120 of the circumferential limiting mechanism CM is slidably disposed on the outer circumferential surface thereof, and is supported by the reference projection 122 on the outer circumferential surface and the axial extension of the inner circumferential surface of the limiting ring 120. The reference slot 126 is non-rotatably connected thereto. Preferably, the centering groove 118 is axially integral with the reference groove 126. The centering projection 68 is provided on the outer peripheral surface of the arm 95 of the intermediate member 90. The force arm 95 preferably has the same structure as the force arm 222 except that there are no teeth 168. At least one of the helical compression spring type elastic members 150 is disposed in a groove on the bottom surface of the tooth of the guide tooth 92, and is axially elastic to the top surface of the guide tooth 52.

显然，由于被制动的袋形导向件 50是一个裸露在外的壳体，因此，如图 2 所示的离心装置式触发机构 AC可直接设置于其上，例如，设置在由其盘形端部 188a内径端轴向延伸出来的端面凸缘上（未示出）。当然，在如后所述的相关变型中，该触发机构 AC也就同时变型为设置在袋形中介件上。 Obviously, since the braked bag-shaped guide 50 is a bare outer casing, the centrifugal-type trigger mechanism AC as shown in FIG. 2 can be directly disposed thereon, for example, disposed at its disc-shaped end. The inner end of the portion 188a extends axially out of the end flange (not shown). Of course, in a related variant as will be described later, the trigger mechanism AC is also modified to be disposed on the pocket-shaped intermediate member.

其次，为适应外壳式导向件 50旋转的特点，摩擦件 70变型为一个盘形圓环，并最佳地借助花键副，不可旋转地连接至由外部轴向延伸至其内孔中的固定轴 240。盘形端部 188b可滑转地设置在固定轴 240的外周面上。 Secondly, in order to accommodate the rotation of the outer casing guide 50, the friction member 70 is modified into a disc-shaped ring and is preferably non-rotatably coupled to the fixing from the outer axial direction to the inner bore thereof by means of a spline pair. Axis 240. The disc-shaped end portion 188b is slidably disposed on the outer peripheral surface of the fixed shaft 240.

另外，用于设置铰接销 28的凸耳，相应地设置在限位环 120的沿盘形端部 188a的外端面内径向延伸的凸缘的内径向凸起上。 Additionally, the lugs for providing the hinge pin 28 are correspondingly disposed on the inner radial projection of the flange of the retaining ring 120 that extends radially within the outer end surface of the disc end 188a.

紧急制动装置 B4的工作过程相同于紧急制动装置 B1 , 此处不再重复。应该指出的是，对应用于高速电梯的情形，应最佳地对紧急制动装置 B4进行回转平衡。例如，在限位环 120内径侧未被填满的入口 82的剩余空间中，设置一个与该剩余空间最佳地具有互补式构造的弧形平衡元件 /配重块。该平衡元件最佳地被贯穿于其中，并固定连接在入口 82两端的轴向孔 51 中的至少一个固定销径向定位。 The emergency brake device B4 works in the same way as the emergency brake device B1 and will not be repeated here. It should be noted that for the case of high speed elevators, the emergency brake B4 should be optimally balanced for swing. For example, in the remaining space of the inlet 82 which is not filled on the inner diameter side of the retaining ring 120, an arc balance element/weight is optimally provided with a complementary configuration to the remaining space. The balancing element is preferably traversed therein and is radially positioned by at least one of the axial pins 51 fixedly coupled to the ends of the inlet 82.

显然，除去弹性元件 150后，紧急制动装置 B4与 B1—样，均将具有实施本发明的最简结构，三个构件以及最简单的操动机构和触发机构 AC。随动齿轮 110、传动轴 210、轴承 158和轴承座 204并非必需，例如应用于自动扶梯时。 It will be apparent that after removal of the resilient member 150, the emergency brake device B4, like B1, will have the simplest construction, three members, and the simplest operating mechanism and trigger mechanism AC for practicing the present invention. The follower gear 110, the drive shaft 210, the bearing 158, and the bearing housing 204 are not necessary, for example, when applied to an escalator.

基于常识，图 8中的导向件 50可以借助诸如精密铸造、浇注、压铸或注塑等方式形成。当然，为了制造的方便，或者为了设置多摩擦片式摩擦机构 F1和 F2的方便，也可将袋形导向件 50变型为由两个不可旋转相连的构件组合成的组合式袋形导向件。其中一个是仅具有轴向力封闭功能的袋形构件式限力元件 180，其中另一个是设置有上述径向力臂的导向件。而且，只需将螺旋花键副由导向件 50与传动轴 210之间，改设至中介件 90与传动轴 210之间，其中的袋形导向件 50就将成为事实上的袋形中介件，或组合式袋形中介件（与摩擦件间接相连）。图 5中的摩擦件 70与限力元件 180的组合，就是组合式袋形摩擦件。进一步地，上述组合式袋形导向件 /中介件中的设置有径向力臂的导向件或中介件，显然也可以作为如图 5 所示的被支撑件，而成为追加的无级支撑机构 SS的组成部分。对应地，应取消弹性元件 150, 而设置如图 5所示的周向限位机构 CM，并将图 8所示的周向限位机构 CM，变型为一个对中式闩锁机构 BL。为此，还需将其对中凸起 68设置在变型后追加的支撑件 220的力臂 222的外周面上。 Based on common knowledge, the guide member 50 in Fig. 8 can be formed by means such as precision casting, casting, die casting or injection molding. Of course, for convenience of manufacture, or for the convenience of providing the multi-friction disc friction mechanisms F1 and F2, the pocket guide 50 can also be modified into a combined pocket guide composed of two non-rotatably connected members. One of them is a bag-shaped force-limiting member 180 having only an axial force closing function, and the other is a guide member provided with the above-described radial force arm. Moreover, it is only necessary to change the helical spline pair between the guiding member 50 and the transmission shaft 210 between the intermediate member 90 and the transmission shaft 210, wherein the pocket-shaped guiding member 50 will become a de facto pocket-shaped intermediate member. , or a combined pocket-shaped interposer (indirectly connected to the friction member). The combination of the friction member 70 and the force limiting member 180 in Fig. 5 is a combined pocket friction member. Further, the guide member or the intermediate member provided with the radial force arm in the above-mentioned combined bag-shaped guide/interposer can obviously be used as the supported member as shown in FIG. 5, and becomes an additional stepless support mechanism. The components of SS. Correspondingly, the elastic member 150 should be eliminated, and the circumferential limiting mechanism CM as shown in FIG. 5 should be provided, and the circumferential limiting mechanism CM shown in FIG. 8 can be modified into a centering latching mechanism BL. For this reason, it is also necessary to arrange the centering projection 68 on the outer peripheral surface of the force arm 222 of the support member 220 which is added after the modification.

不难理解，如果将图 8中的基准凸起 122和基准槽 126, 分别如图 2所示地设置在限位环 120的内径向凸缘与传动轴 210之间，那么由上述说明可知，基准凸起 122或基准槽 126中的一个，将以不可旋转相连接的形式，事实上间接地设置在导向件或中介件中的一个上。 It is not difficult to understand that if the reference projection 122 and the reference groove 126 in FIG. 8 are respectively disposed between the inner radial flange of the retaining ring 120 and the transmission shaft 210 as shown in FIG. 2, it will be understood from the above description. One of the reference projections 122 or the reference slots 126 will be in a non-rotatable phase connection, in fact indirectly disposed on one of the guides or intermediate members.

如前文所述，虽非最佳，但依据本发明的紧急制动装置，其摩擦件 70显然也可用作被制动的转矩输入构件。例如，将图 8 中的固定轴 240与传动轴 210 的作用互换，取消其触发机构 AC,在限位环 120的内径向凸缘与盘形端部 188a 之间设置膜片式蓄能弹簧，在盘形端部 188b外端面和旋转的固定轴 240上，分别设置如图 7所示的闩锁机构 BL和触发机构 AC：。其中，闩锁机构 BL的触发件 130的卡爪 132，可转动地卡合在由限位环 120的相应端部轴向延伸出来的凸起的周向或内径向的钩爪与盘形端部 188b之间，从而轴向阻挡住限位环 120弹性缩回的趋势，直至被离心式触发机构 AC触发或被其它信号触发为止。 As described above, although not optimal, the friction member 70 of the emergency brake device according to the present invention can obviously also be used as the torque input member to be braked. For example, the function of the fixed shaft 240 in FIG. 8 is interchanged with the function of the drive shaft 210, the trigger mechanism AC is eliminated, and a diaphragm type energy storage spring is disposed between the inner radial flange of the retaining ring 120 and the disc-shaped end portion 188a. On the outer end surface of the disc-shaped end portion 188b and the rotating fixed shaft 240, a latch mechanism BL and a trigger mechanism AC: as shown in FIG. 7 are respectively disposed. Wherein, the claws 132 of the triggering member 130 of the latching mechanism BL are rotatably engaged with the circumferential or inner radial claws and the disc-shaped end extending axially from the respective ends of the limiting ring 120. Between the portions 188b, thereby axially blocking the tendency of the limit ring 120 to elastically retract until it is triggered by the centrifugal trigger mechanism AC or triggered by other signals.

显然地，如果再将导向件 50如上文所述地变型为事实上的袋形中介件或组合式袋形中介件，那么，闩锁机构 BL便是直接或间接地设置在该中介件上。 Obviously, if the guide member 50 is again modified as described above as a de facto pocket-shaped intermediate member or a combined pocket-shaped intermediate member, the latching mechanism BL is disposed directly or indirectly on the intermediate member.

无疑，该变型中的离心式触发机构 AC、闩锁机构 BL和周向限位机构 CM, 也可用于图 5所示的紧急制动装置 B2中，取代相应机构以控制支撑件 220的周向位置。当然，单向制动时，周向限位机构 CM应最佳地变型为槽道式圓柱凸轮机构，以省去弹性元件 150。其中，限位环 120显然就是该机构的移动件。 Undoubtedly, the centrifugal trigger mechanism AC, the latch mechanism BL and the circumferential limit mechanism CM in this modification can also be used in the emergency brake device B2 shown in FIG. 5 instead of the corresponding mechanism to control the circumferential direction of the support member 220. position. Of course, in the case of one-way braking, the circumferential limit mechanism CM should be optimally modified into a channel-type cylindrical cam mechanism to eliminate the elastic member 150. Among them, the limit ring 120 is obviously the moving part of the mechanism.

工业适用性 Industrial applicability

如上所述，依据本发明的紧急制动装置，显然具有普适于卷扬、提升和牵引设备领域的综合能力。而且凭借其优越的技术性能、使用性能以及成本优势，其最适合取代现有技术和相关产品，通用于包括基于钢绳曳引式、链条驱动式以及齿轮齿条驱动式的各种垂直电梯、自动扶梯或移动人行道，以用于它们的防断绳 /断链、防超速、防逆转、防故障断电和正常停电 /停机时的紧急制动和工作制动。另外，也可用作各种热动力原动机等的防飞车 /速制动器。 As described above, the emergency brake device according to the present invention clearly has a comprehensive ability in the field of hoisting, lifting and pulling equipment. And with its superior technical performance, performance and cost advantages, it is best suited to replace the existing technology and related products, and is generally used in various vertical elevators including steel rope traction, chain drive and rack and pinion drive. Escalators or moving walkways for their anti-break rope/chain breaking, anti-overspeed, anti-reverse, fail-safe power outages and emergency and work brakes during normal power outages/downtimes. In addition, it can also be used as an anti-speed/speed brake for various thermodynamic prime movers.

以上仅仅是本发明针对其有限实施例给予的描迷和图示，具有一定程度的特殊性，但应该理解的是，所提及的实施例和附图都仅仅用于说明的目的，而不用于限制本发明及其保护范围，其各种变化、等同、互换以及更动结构或各构件的布置，都将被认为未脱离开本发明构思的精神和范围。 The above is only a description and illustration of the invention given for its limited embodiments, with a certain degree of particularity, but it should be understood that the embodiments and drawings are for illustrative purposes only and are not used. The scope of the present invention and its scope of the invention are to be construed as being limited by the scope of the invention.

Claims

权利要求书 Claim

1. 一种升降设备用空间楔合式防坠落、防超速紧急制动装置，包括：绕一轴线回转且可轴向接合的至少一个牵引摩擦机构，其具有绕所述轴线回转并均设置有摩擦面的至少大致为环状的中介件和摩擦件 , 以在该两构件间传递摩擦转矩； A space wedge-type fall arresting/anti-overspeed emergency braking device for a lifting device, comprising: at least one traction friction mechanism that is pivoted about an axis and axially engageable, having a rotation about the axis and both being provided with friction At least substantially annular intermediate and friction members for transmitting frictional torque between the members;

为所述牵引摩擦机构提供接合力并绕所述轴线回转的至少一个转动导向机构，其具有绕所述轴线回转并均设置有相应导向面的至少大致为环状的导向件和所述中介件；以及 Providing at least one rotational guiding mechanism for the traction friction mechanism to rotate and rotate about the axis, having at least substantially annular guide members and the intermediate member that are rotated about the axis and each provided with a corresponding guiding surface ; as well as

至少间接地设置在所述导向件、所述中介件和所述摩擦件中的一个之上的操动机构，用以至少间接地控制所述中介件的入楔动作； An operating mechanism disposed at least indirectly on one of the guide member, the intermediate member and the friction member for at least indirectly controlling a wedge action of the intermediate member;

至少间接地设置在所述导向件、所述中介件和所述摩擦件中的一个之上的触发机构，其响应于输入信号而促动所述操动机构，以至少间接地致使所述中介件入楔，从而致动所述紧急制动装置； a trigger mechanism disposed at least indirectly over one of the guide member, the intermediate member and the friction member, responsive to an input signal to actuate the operating mechanism to at least indirectly cause the intermediary Inserting a wedge into the wedge to actuate the emergency braking device;

当所述导向件和所述摩擦件被所述中介件可驱动地连接成一个摩擦体时，于零且 '、于 ^于 ξ , 即， ο < λ '< ξ , 其^ , ξ是能够令形成于所述 4氏触部位的导向摩擦副自锁的所述升角 λ的最大值。 When the guide member and the friction member are drivingly coupled to the friction member by the intermediate member, at zero, and then, ο < λ '< ξ, The maximum value of the lift angle λ of the self-locking of the guide friction pair formed at the four-contact portion.

2. 按权利要求 1所述的紧急制动装置，其特征在于：该紧急制动装置包括两个绕所述轴线回转的可轴向接合的摩擦机构，其中一个是所述牵引摩擦机构 , 其中另一个是与所述导向件和所述摩擦件至少不可旋转地分别结合在一起的传力摩擦机构以及再一个所述牵引摩擦机构中的一个。 2. The emergency brake device according to claim 1, wherein: the emergency brake device includes two axially engageable friction mechanisms that rotate about the axis, one of which is the traction friction mechanism, wherein The other is a force transmitting friction mechanism and at least one of the traction friction mechanisms that are respectively non-rotatably coupled to the guide member and the friction member.

3. 按权利要求 1所述的紧急制动装置，其特征在于：所述升角 λ大于 ζ , 即， ζ < λ ξ , 其中， ζ是能够令所述抵触部位的导向摩擦副自锁的所述升角 λ的最小值，也是令所述牵引摩擦机构的牵引摩擦副自锁的所述升角 λ的最大值， ξ的含义同上。 3. The emergency brake device according to claim 1, wherein: said raising angle λ is greater than ζ, that is, ζ < λ ξ , wherein ζ is capable of self-locking the guiding friction pair of said abutting portion The minimum value of the lift angle λ is also the maximum value of the lift angle λ of the traction friction pair of the traction friction mechanism, and the meaning of ξ is the same as above.

4. 按权利要求 1所述的紧急制动装置，其特征在于：当 ζ > 0时，所述升角 λ小于等于 ζ，即， 0 < λ < ζ , 其中， ζ的含义同上。 4. The emergency brake device according to claim 1, wherein: when ζ > 0, said rising angle λ is less than or equal to ζ, that is, 0 < λ < ζ , wherein ζ has the same meaning as above.

5. 按权利要求 1所述的紧急制动装置，其特征在于： 5. The emergency brake device of claim 1 wherein:

还包括至少一个限力元件；以及 Also including at least one force limiting element;

所述导向件、所述中介件和所述摩擦件中的至多一个，是至少通过不可旋转的连接方式包括有所述限力元件的力封闭式组合构件，以建立相互之间的轴向力封闭式抵触连接。 At least one of the guide member, the intermediate member and the friction member is a force-closed composite member including the force-limiting member at least by a non-rotatable connection to establish an axial force between each other Closed conflicting connection.

6. 按权利要求 1 ~ 5任一项所述的紧急制动装置，其特征在于：所述导向件、所述中介件、所述摩擦件和所述限力元件之一是袋形构件，用以建立相互之间的轴向力封闭式抵触连接，其设置有绕所述轴线回转的至少大致半周的内周面，以及位于该内周面上的大致半周的周向凹槽和由所述袋形构件的外周面连通至该周向凹槽的入口。 The emergency brake device according to any one of claims 1 to 5, characterized in that: One of the intermediate member, the friction member and the force limiting member is a pocket member for establishing an axial force closed contact connection with each other, which is provided with at least approximately a revolution about the axis A semicircular inner peripheral surface, and a substantially half-circumferential circumferential groove on the inner peripheral surface and an inlet connected to the circumferential groove by the outer peripheral surface of the pocket member.

7. 按权利要求 1 ~ 5任一项所述的紧急制动装置，其特征在于：所述触发机构包括离心装置，其具有离心配重，限力弹簧，以及绕所述轴线且至少间接地设置在转动件上的随动座环，以响应于该转动件超过设定转速时的离心力而动作，所述转动件是所述导向件、所述中介件和所述摩擦件中的一个。 The emergency brake device according to any one of claims 1 to 5, wherein: the trigger mechanism comprises a centrifugal device having a centrifugal weight, a force-limiting spring, and at least indirectly around the axis a follower seat ring disposed on the rotating member to act in response to a centrifugal force when the rotating member exceeds a set rotational speed, the rotating member being one of the guide member, the intermediate member, and the friction member.

8. 按权利要求 7所述的紧急制动装置，其特征在于：还包括受所述触发机构控制的闩锁机构，其至少间接地设置在所述导向件、所述中介件和所述摩擦件中的一个上，以在闭锁工况中，持续地约束住所述操动机构，进而维持住所述中介件的解楔状态，而在受到所述触发机构促动后的解锁工况中，则持续地解除其对所述操动机构的所述约束，以至少间接地致使所述中介件入楔。 8. The emergency brake device of claim 7 further comprising: a latching mechanism controlled by said triggering mechanism, at least indirectly disposed on said guide member, said intermediate member and said friction One of the pieces, in the blocking condition, continuously restraining the operating mechanism, thereby maintaining the unwound state of the intermediate member, and in the unlocking condition after being actuated by the triggering mechanism, The constraint on the operating mechanism is continuously released to at least indirectly cause the interposer to wedge.

9. 按权利要求 7所述的紧急制动装置，其特征在于：所述操动机构包括周向自由度大于等于零的周向限位机构，该周向限位机构具有至少一个限位凸起，以及可对应地收纳该限位凸起的限位凹槽，两者至少间接地分别设置在所述中介件和所述导向件上；当所述限位凸起收纳至所述限位凹槽时，所述中介件在两个圓周方向上均不能自由地入楔。 9. The emergency brake device according to claim 7, wherein: the operating mechanism comprises a circumferential limit mechanism having a circumferential degree of freedom greater than or equal to zero, the circumferential limit mechanism having at least one limit projection And a limiting groove correspondingly accommodating the limiting protrusion, at least indirectly disposed on the intermediate member and the guiding member; when the limiting protrusion is received into the limiting recess In the case of the groove, the intermediate member is not free to enter the wedge in both circumferential directions.

10. 按权利要求 9 所述的紧急制动装置，其特征在于：所迷限位凸起至少具有周向弹性，所述周向限位机构的周向自由度等于零。 10. The emergency brake device according to claim 9, wherein: the limiting projection has at least circumferential elasticity, and the circumferential freedom of the circumferential limiting mechanism is equal to zero.

11. 按权利要求 8 所述的紧急制动装置，其特征在于：所述操动机构包括绕所述轴线设置的无级支撑机构，其设置在所述限力元件和被支撑件之间，以轴向无级地移动该被支撑件的方式，建立所述限力元件与所述导向件、所述中介件以及所述摩擦件之间的轴向力封闭式抵触连接；所述被支撑件是所述导向件、所述中介件和所述摩擦件中与所述限力元件不可旋转相连的那一个。 11. The emergency brake device according to claim 8, wherein: the operating mechanism includes a stepless support mechanism disposed around the axis, and is disposed between the force limiting member and the supported member. Establishing an axial force closed contact connection between the force limiting member and the guide member, the intermediate member and the friction member in a manner of axially steplessly moving the supported member; The member is the one of the guide member, the intermediate member and the friction member that is non-rotatably connected to the force limiting member.

12. 按权利要求 11所述的紧急制动装置，其特征在于： 12. The emergency brake device of claim 11 wherein:

所述无级支撑机构包括绕所述轴线设置且至少呈大致环状的支撑件，其通过轴向抵触和转动导向两种连接方式，分别连接至所述限力元件和所述被支撑件，其外周面上设置有部分轮齿； The stepless support mechanism includes a support member disposed around the axis and having at least a substantially annular shape, which is connected to the force limiting member and the supported member by an axially abutting and a rotating guide. a part of the teeth are arranged on the outer peripheral surface thereof;

所述无级支撑机构还包括作用至所述支撑件的蓄能弹簧，其用于将所述支撑件持续地弹压向可以致使所述无级支撑机构建立所述轴向力封闭式抵触连接的方向； The stepless support mechanism further includes an energy storage spring acting on the support member for continuously biasing the support member to cause the stepless support mechanism to establish the axial force closed contact connection Direction

所述支撑件相对所述限力元件的周向自由度，至少大到致使所述无级支撑机构可以建立所述轴向力封闭式抵触连接的程度。 The circumferential freedom of the support member relative to the force limiting member is at least as large as to enable the stepless support mechanism to establish the extent of the axial force closed contact connection.

13. 按权利要求 11所述的紧急制动装置，其特征在于：所述闩锁机构包括：可转动地设置在所述限力元件上的行星组合轮，其位于所述限力元件内部的部分，固定有啮合至所述支撑件的所述部分轮齿的行星齿轮，其位于所述限力元件外部的部分，固定有锁止件； 13. The emergency brake device according to claim 11, wherein: the latch mechanism includes: a planetary combination wheel rotatably disposed on the force limiting member, located inside the force limiting member a portion, a planetary gear that is engaged with the partial gear teeth of the support member, and a portion of the planetary gear that is external to the force limiting member, is fixed with a locking member;

可转动地设置在所述限力元件上的触发件，被所述触发机构触发之前，该触发件可维持与所述锁止件的卡合，以持续阻止所述锁止件的自转，被所述触发机构触发之后，该触发件将解除其与所述锁止件的所述卡合。 a trigger member rotatably disposed on the force-limiting member, the trigger member can maintain engagement with the lock member to continuously prevent rotation of the lock member before being triggered by the trigger mechanism After the trigger mechanism is triggered, the trigger member will release its engagement with the locking member.

14. 按权利要求 8所述的紧急制动装置，其特征在于： 14. The emergency brake device of claim 8 wherein:

所述操动机构包括摩擦式止转机构，其具有不可旋转地和至少间接地设置在所述摩擦件上的至少一个止转件，用以受控地摩擦抵触至所述中介件，以及将所述止转件持续地弹压向所述中介件的蓄能弹簧； The operating mechanism includes a friction type anti-rotation mechanism having at least one anti-rotation member that is non-rotatably and at least indirectly disposed on the friction member for controlled frictional contact with the interposer, and The rotation preventing member continuously elastically presses the energy storage spring of the intermediate member;

所述闩锁机构包括，触发件，其可转动地和至少间接地设置在所述摩擦件上，被所述触发机构触发之前，该触发件可维持与所述止转件的至少间接的卡合，以持续阻止所述止转件的移动，被所述触发机构触发之后，该触发件将解除其与所述止转件的所述卡合。 The latch mechanism includes a trigger member rotatably and at least indirectly disposed on the friction member, the trigger member maintaining at least an indirect card with the rotation member before being triggered by the trigger mechanism In order to continuously prevent the movement of the anti-rotation member, after being triggered by the trigger mechanism, the trigger member will release the engagement with the anti-rotation member.

15. 按权利要求 8 所述的紧急制动装置，其特征在于：所迷操动机构包括圓柱凸轮机构和周向限位机构之一，该两个机构均具有至少一个凸起，以及可对应地收纳该凸起的凹槽，两者至少间接地分别设置在所述中介件和所述导向件中的一个之上，以及与其中的另一构件不可旋转相连的移动件之上；该两个机构均还具有至少一个蓄能弹簧，其用于将所述移动件持续地弹压向可以致使所述中介件入楔的方向；而当所述凸起收纳至所述凹槽时，所述中介件在两个圓周方向上均不能自由地入楔。 15. The emergency brake device according to claim 8, wherein: the operating mechanism comprises one of a cylindrical cam mechanism and a circumferential limiting mechanism, each of the two mechanisms having at least one protrusion and corresponding Storing the raised recesses, at least indirectly disposed on one of the intermediate member and the guide member, and on a moving member that is non-rotatably coupled to another member thereof; Each of the mechanisms further has at least one energy storage spring for continuously biasing the moving member toward a direction that can cause the intermediate member to enter the wedge; and when the projection is received into the groove, the The interposer is not free to enter the wedge in both circumferential directions.

16. 按权利要求 1 ~ 5任一项所述的紧急制动装置，其特征在于：所述输入信号至少包括机械信号和电信号之一，并至少响应于驱动用钢丝绳断开，驱动用链条断开，所述升降设备的运行方向和速度不符合设定值，非正常断电，正常停电以及正常停机中的一种情形而产生。 The emergency brake device according to any one of claims 1 to 5, wherein: the input signal includes at least one of a mechanical signal and an electrical signal, and at least in response to the driving wire rope being disconnected, the driving chain Disconnected, the running direction and speed of the lifting device do not meet the set value, abnormal power off, normal power outage and normal shutdown.

17. 按权利要求 1 ~ 5任一项所述的紧急制动装置，其特征在于： The emergency brake device according to any one of claims 1 to 5, characterized in that:

设置有两个径向上相互嵌套的所述转动导向机构，该两机构的两个所述导向件以及两个所述中介件，以所述导向面位于同方向端面上的形式，分别连接成刚性一体，以及不可旋转地连接成周向一体； Provided are two rotating guiding mechanisms which are mutually nested in a radial direction, and the two guiding members and the two intermediate members of the two mechanisms are respectively connected in the form of the guiding surfaces on the same direction end faces. Rigidly integrated, and non-rotatably connected in a circumferential direction;

两个所述转动导向机构中各自的所述导向摩擦副的升角 λ , 分别大于零且小于等于 ζ，以及大于 ζ且小于等于 ξ ; The rising angles λ of the respective guiding friction pairs of the two rotating guiding mechanisms are respectively greater than zero and less than or equal to ζ, and greater than ζ and less than or equal to ξ;

设置有至少一个弹性元件，其轴向上至少间接地抵触至所述升角 λ大于零且小于等于 ζ的所述转动导向机构。 At least one elastic element is provided which axially at least indirectly interferes with the rotational guiding mechanism with the lifting angle λ being greater than zero and less than or equal to ζ.

18. 按权利要求 1 ~ 5任一项所述的紧急制动装置，其特征在于：还包括至少具有一个弹性元件的弹性预紧机构，其用于持续地保持所述中介件与所述摩擦件之间的至少间接的摩擦连接。 The emergency brake device according to any one of claims 1 to 5, further comprising: an elastic pretensioning mechanism having at least one elastic member for continuously maintaining the intermediate member and the friction At least an indirect frictional connection between the pieces.

19. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述导向件和所述中介件的所述导向面是螺旋型齿面，其设置在该二构件的包括端面、内周面和外周面的一个表面上；在轴平面内，该螺旋型齿面与所述轴线之间的夹角大于 0度，小于 180度。 The emergency brake device according to any one of claims 1 to 7, wherein: the guiding surface of the guiding member and the intermediate member is a spiral tooth surface, which is disposed on the two members The surface including the end surface, the inner circumferential surface and the outer circumferential surface; in the axial plane, the angle between the spiral tooth surface and the axis is greater than 0 degrees and less than 180 degrees.

20. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述限力元件是具有中心圆孔的杯形壳。 The emergency brake device according to any one of claims 1 to 7, wherein the force limiting member is a cup-shaped casing having a center circular hole.

21. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述限力元件包括径向上至少大致对称的两个半圓壳和至少一个环形箍，该两个半圓壳的形状具有这样的组合效果，即，二者径向对接所构成的组合构件，设置有绕所述轴线的中心圓孔以及位于该中心圓孔内周面上的绕所述轴线的周向凹槽；所述环形箍设置在所述组合构件的中部和外端部之一的外周面上，以固定所述组合构件。 The emergency brake device according to any one of claims 1 to 7, characterized in that the force-limiting element comprises two semi-circular shells and at least one annular hoop which are at least substantially symmetrical in the radial direction, the two semi-circular shells The shape has a combined effect, that is, the combined member formed by the radial abutting thereof is provided with a central circular hole around the axis and a circumferential groove around the axis on the inner circumferential surface of the central circular hole; The annular hoop is disposed on an outer peripheral surface of one of a central portion and an outer end portion of the composite member to fix the combined member.

22. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述牵引摩擦机构和所述传力摩擦机构中的至少一个，其两个相应摩擦面是半锥顶角大于 0度而小于 180度的截锥面。 The emergency brake device according to any one of claims 1 to 7, characterized in that: at least one of the traction friction mechanism and the force transmitting friction mechanism, the two corresponding friction surfaces are half cone tops A truncated cone with an angle greater than 0 degrees and less than 180 degrees.

23. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述牵引摩擦机构是多摩擦片式摩擦机构，其具有与所述摩擦件和所述中介件分别不可旋转地相连接的两组轴向交错排列的各至少一个摩擦片。 The emergency brake device according to any one of claims 1 to 7, wherein: the traction friction mechanism is a multi-friction disc type friction mechanism, which is different from the friction member and the intermediate member. Rotatingly connected two sets of at least one friction lining that are axially staggered.

24. 按权利要求 1 ~ 7任一项所述的紧急制动装置，其特征在于：所述传力摩擦机构是多摩擦片式摩擦机构，其具有与所述摩擦件和所述导向件分别不可旋转地相连接的两组轴向交错排列的各至少一个摩擦片。 The emergency brake device according to any one of claims 1 to 7, wherein: the force transmitting friction mechanism is a multi-friction disc type friction mechanism having a friction member and the guide member respectively Two sets of at least one friction plate that are non-rotatably connected to each other in an axially staggered arrangement.