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WO2012089130A1 - Dispositif de protection antichute à coin spatial et dispositif de freinage d'urgence anti excès de vitesse utilisé dans un appareil de levage - Google Patents

Dispositif de protection antichute à coin spatial et dispositif de freinage d'urgence anti excès de vitesse utilisé dans un appareil de levage Download PDF

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Publication number
WO2012089130A1
WO2012089130A1 PCT/CN2011/084842 CN2011084842W WO2012089130A1 WO 2012089130 A1 WO2012089130 A1 WO 2012089130A1 CN 2011084842 W CN2011084842 W CN 2011084842W WO 2012089130 A1 WO2012089130 A1 WO 2012089130A1
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WO
WIPO (PCT)
Prior art keywords
friction
force
brake device
circumferential
emergency brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2011/084842
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English (en)
Chinese (zh)
Inventor
洪涛
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2012089130A1 publication Critical patent/WO2012089130A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B5/00—Applications of checking, fault-correcting, or safety devices in elevators
    • B66B5/02—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions
    • B66B5/04—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions for detecting excessive speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B5/00—Applications of checking, fault-correcting, or safety devices in elevators
    • B66B5/02—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions
    • B66B5/16—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well
    • B66B5/18—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well and applying frictional retarding forces

Definitions

  • 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 .
  • 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
  • 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.
  • 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.
  • the torque capacity is relatively small and the structure is complicated.
  • 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).
  • an active brake such as spring force
  • 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.
  • 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.
  • the present invention is directed to designing a brake device based on a completely new technical principle to avoid the above disadvantages.
  • 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.
  • 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;
  • the friction member is drivingly coupled to form
  • 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.
  • the range of the rising angle ⁇ may further be: ⁇ ⁇ ⁇ ⁇ , or 0 ⁇ ⁇ ⁇ (when ⁇ > 0 ), wherein ⁇ is capable of self-locking the guiding friction pair of the abutting portion
  • the minimum value of the lift angle ⁇ is also the maximum value of the lift angle ⁇ of the traction friction pair of the traction friction mechanism.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the force limiting element is a cup-shaped shell having a central circular aperture.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the limiting projection has at least circumferential elasticity, and the circumferential freedom of the circumferential limiting mechanism is equal to zero.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ⁇ of the friction pair is greater than zero and less than or equal to ⁇ , and greater than ⁇ and less than or equal to ⁇ ; the elastic element axially at least indirectly interferes with the turning guide mechanism having an angle of rise ⁇ greater than zero and less than or equal to ⁇ .
  • 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.
  • 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.
  • 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.
  • Space wedge mechanism A mechanism consisting of a rotary guide mechanism and a traction friction mechanism.
  • 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.
  • ⁇ and ⁇ 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
  • 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.
  • 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.
  • the space wedge mechanism is in a half-wedge state and the emergency brake device is in a non-fully engaged state.
  • 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 ⁇ 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.
  • the above-mentioned rising angle ⁇ is the wedge angle of the space wedge mechanism, also called the wedge angle/crowding angle, and only when 0 ⁇ ⁇ ⁇ , the space wedge mechanism can be wedged, and the emergency braking device can be engaged.
  • the space-wedge emergency braking device 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.
  • FIG. 1 is a schematic view showing the layout of an elevator system layout to which the present invention is applied.
  • Figure 2 is an axial sectional view of an emergency brake device according to a first embodiment of the present invention.
  • 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.
  • Figure 5 is a simplified axial cross-sectional view of an emergency braking device in accordance with a second embodiment of the present invention.
  • Figure 6 is a partial schematic view of the right side view of Figure 5.
  • Figure ⁇ is a simplified axial cross-sectional view of an emergency braking device in accordance with a third embodiment of the present invention.
  • 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
  • Embodiment 1 Centering emergency brake device B1
  • 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.
  • a known back wheel (not shown) is provided to ensure reliable engagement.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the axially closed bag-shaped friction member 70 can also be a composite member.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a radial notch can be provided at one axial end of the inlet 82.
  • 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.
  • 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.
  • 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.
  • the intervening member 90 can be wedged by means of circumferential inertia or by a special setting of the angle ⁇ of 0 ⁇ ⁇ , 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.
  • 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.
  • 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
  • a pair of surface-contacting spiral guide friction pairs corresponding to different circumferential directions can be formed.
  • the two complementary elevation angles ⁇ 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 ⁇ .
  • one of the rising angles ⁇ ⁇ ⁇ ⁇ can be optimally equal to 90 degrees parallel to the axis X.
  • 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.
  • 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 ⁇ is optimally greater than zero to ensure that the circumferential freedom/gap of the rotational guiding mechanism G can be equal to the order.
  • 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.
  • the tooth height and the tooth width of all of the guide teeth 52 and 92 are set such that the axial freedom ⁇ 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 ⁇ 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.
  • 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.
  • 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.
  • 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 ⁇ /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 4 ⁇ .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • the actuating ring 48 is optimally spaced from the radial face 42 of the sector link 40.
  • 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.
  • 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.
  • 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.
  • a parallel triggering power to carry out emergency braking can also be given to the passengers in the car.
  • 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.
  • 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.
  • centrifugal devices are also known for more than one.
  • 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.
  • the working process of the emergency brake device B1 is very simple.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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.
  • the emergency brake device B1 can obtain the friction braking function adaptively relative to the driving torque overload slip only in the setting with ⁇ ⁇ ⁇ ⁇ , 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.
  • 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.
  • the adaptive ABS anti-lock is obtained with a purely mechanical structure with rigid wedges. Dead braking effect.
  • 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.
  • the emergency brake device B1 having 0 ⁇ ⁇ ⁇ ⁇ (for the case of ⁇ > 0) will have the non-slip/moving instantaneous stop function as described above, and the inelastic buffer in the prior art.
  • the car is subjected to a large impact.
  • 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).
  • 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.
  • 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.
  • 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.
  • the emergency brake device B1 when 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the function of stopping the escalation of the escalator is realized, and there is no possibility of any impact.
  • 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.
  • 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.
  • 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.
  • 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.
  • the emergency braking device 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.
  • the limit ring 120 is triggered.
  • 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.
  • the actuating ring 48 is modified to abut against the radial lugs of the stop ring 120.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the present invention also has various techniques for increasing the limit angle ⁇ and ⁇ values in order to achieve greater design freedom and to make the space wedge mechanism easier to wedge or unwrap.
  • the guide faces 54 and 94 of the rotary guide mechanism G are disposed as inclined spiral tooth faces
  • 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.
  • the static friction coefficient is 0.10
  • the ⁇ and ⁇ 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Embodiment 2 Stepless support emergency brake device B2
  • 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.
  • the emergency brake device B2 is a parallel space wedge mechanism including two rotary guide mechanisms.
  • the guide teeth 92a and 52a of the rotary guide mechanism Ga having 0 ⁇ ⁇ ⁇ 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 ⁇ ⁇ ⁇ ⁇ ⁇ 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 least one elastic member 100 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • 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 ⁇ ', 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.
  • the guide teeth 62 and 232 can also be disposed on the support end faces 224 and 189, respectively. Referring to Fig.
  • the guide teeth 62 and 232 are preferably serrated, both of which are provided with a helical guide surface having an angle of elevation ⁇ ' ⁇ ⁇ ', preferably parallel to the non-guide surface of the axis X.
  • ⁇ ' has the same definition as ⁇ .
  • 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 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.
  • 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.
  • 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 ⁇ ', 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.
  • 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 ⁇ ' in the circumferential groove 78 greater than zero, but less than or equal to the rotation corresponding to the circumferential freedom ⁇ '
  • the axial movement distance of the guiding motion is ⁇ ' X tg ⁇ '.
  • 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 ⁇ ' in the non-braking disengaged state is located between the friction surfaces of the friction mechanism F1 or F2.
  • 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.
  • 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.
  • 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.
  • the lock member 164 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.
  • the locking member 164 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.
  • the friction member 70 Under the action of the rotation guiding mechanism UG, the friction member 70 will be immediately derived by the distance of ⁇ ' 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.
  • 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.
  • the emergency brake device ⁇ 2 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.
  • the trigger member 130 is preferably a " ⁇ " 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.
  • 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.
  • the movable weight mechanism 21 is provided.
  • the spring force provided by the energy storage spring 156 should be optimally maximized.
  • 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.
  • the turning guide mechanism G is a one-way mechanism, it is not necessary to use an elastic force to unwrap the wedge.
  • Embodiment 3 Forced anti-rotation emergency brake device B3
  • 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.
  • 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.
  • the pin 172 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.
  • 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.
  • the taper of the truncated cone 106 is optimally ensured to be frictionally self-locking with the anti-rotation member 170.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • the trigger mechanism AC is also modified to be disposed on the pocket-shaped intermediate member.
  • 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.
  • the disc-shaped end portion 188b is slidably disposed on the outer peripheral surface of the fixed shaft 240.
  • 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.
  • 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.
  • 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.
  • the guide member 50 in Fig. 8 can be formed by means such as precision casting, casting, die casting or injection molding.
  • 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.
  • 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.
  • 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 are 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.
  • 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.
  • the centering projection 68 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.
  • 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.
  • the friction member 70 of the emergency brake device can obviously also be used as the torque input member to be braked.
  • 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.
  • a latch mechanism BL and a trigger mechanism AC are respectively disposed.
  • 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.
  • the latching mechanism BL is disposed directly or indirectly on the intermediate member.
  • 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.
  • the circumferential limit mechanism CM should be optimally modified into a channel-type cylindrical cam mechanism to eliminate the elastic member 150.
  • the limit ring 120 is obviously the moving part of the mechanism.
  • the emergency brake device 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

Fait l'objet de cette invention un dispositif de protection antichute à coin spatial et de freinage d'urgence anti excès de vitesse utilisé dans un appareil de levage, comprenant un mécanisme de commande de coin qui comprend, à son tour, un mécanisme opérationnel et un mécanisme d'enclenchement (AC), ainsi qu'un mécanisme de freinage à coin spatial rotatif tenant lieu de mécanisme d'accouplement frictionnel d'autoserrage à force axiale de type fermé doté d'une capacité de couple à forte résistance. L'invention comprend aussi un mécanisme guide rotatif (G) constitué de pièces guides (50) à surface guide spiralée et de pièces intermédiaires (90), ainsi que deux mécanismes de frottement rotatifs (F1, F2) à contact par surface constitués de pièces de frottement (70) disposées par rapport aux pièces guides (50) et aux pièces intermédiaires (90). Ce mécanisme de freinage à coin comprend un mécanisme d'enclenchement (AC) centrifuge purement mécanique et un mécanisme d'écartement périphérique de manière à assembler les mécanismes de commande et de freinage. Le mécanisme d'enclenchement (AC) réagit d'une part au mouvement centrifuge et d'autre part au signal de rupture de filin/chaîne, au signal électronique d'excès de vitesse, aux coupures de courant causées par une panne et au signal électronique de type coupure de courant et temps d'arrêt normaux. Ce dispositif de freinage d'urgence s'utilisant sur les dispositifs de levage fait preuve d'une fiabilité et sécurité élevées, présente une structure simple, est compact et peu coûteux.
PCT/CN2011/084842 2010-12-30 2011-12-28 Dispositif de protection antichute à coin spatial et dispositif de freinage d'urgence anti excès de vitesse utilisé dans un appareil de levage Ceased WO2012089130A1 (fr)

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CN201010624779.6 2010-12-30
CN201010624779.6A CN102556798B (zh) 2010-12-30 2010-12-30 升降设备用空间楔合式防坠落、防超速紧急制动装置

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CN105752791A (zh) * 2016-03-23 2016-07-13 安徽瑞格电梯服务股份有限公司 一种电梯制动设备
CN111483901A (zh) * 2019-01-02 2020-08-04 奥的斯电梯公司 电梯安全装置

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CN107215743B (zh) * 2017-07-25 2022-12-09 波士顿电梯（湖州）有限公司 防坠电梯
CN107884169B (zh) * 2017-11-07 2019-12-24 叶豪 一种用于防坠安全器的转矩转速测量装置
CN109264524B (zh) * 2018-09-13 2021-01-26 日立楼宇技术（广州）有限公司 振动器、电梯轿厢振动实验系统及其控制方法
CN109908506B (zh) * 2019-04-03 2024-04-26 江苏伯尔特新型材料有限公司 一种轨道制动防坠落装置
CN109908505A (zh) * 2019-04-03 2019-06-21 江苏伯尔特新型材料有限公司 一种高效轨道制动防坠落装置
CN110040598B (zh) * 2019-05-15 2024-01-09 广州广日电梯工业有限公司 一种无级触发的限速装置
CN115362115B (zh) * 2020-02-14 2025-06-24 维托控股有限公司 用于致动电梯制动器的触发单元
CN111731978B (zh) * 2020-07-01 2022-01-28 浙江科技学院 具有均匀受载与减振保护功能的新型限速器及其工作方法
CN112504600B (zh) * 2020-11-30 2022-09-27 中国工程物理研究院总体工程研究所 一种火箭撬的导向滑靴
CN112744661B (zh) * 2021-01-12 2025-01-07 菲尼克斯电梯有限公司 一种带有紧急制动机构的电梯

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FR2548301A1 (fr) * 1983-07-02 1985-01-04 Fichtel & Sachs Ag Embrayage a ressort diaphragme comprime, avec rattrapage automatique de l'usure dans la region du cercle de pivotement
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CN105752791A (zh) * 2016-03-23 2016-07-13 安徽瑞格电梯服务股份有限公司 一种电梯制动设备
CN111483901A (zh) * 2019-01-02 2020-08-04 奥的斯电梯公司 电梯安全装置
CN111483901B (zh) * 2019-01-02 2022-02-11 奥的斯电梯公司 电梯安全装置

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