EP4003896B1 - Hebezeug - Google Patents

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Publication number
EP4003896B1
EP4003896B1 EP20708417.9A EP20708417A EP4003896B1 EP 4003896 B1 EP4003896 B1 EP 4003896B1 EP 20708417 A EP20708417 A EP 20708417A EP 4003896 B1 EP4003896 B1 EP 4003896B1
Authority
EP
European Patent Office
Prior art keywords
locking
disc
lifting gear
control
disk
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.)
Active
Application number
EP20708417.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP4003896A1 (de
EP4003896C0 (de
Inventor
Detlef Struck
Wolfram SCHNEEBECK
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Columbus McKinnon Industrial Products GmbH
Original Assignee
Columbus McKinnon Industrial Products GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Columbus McKinnon Industrial Products GmbH filed Critical Columbus McKinnon Industrial Products GmbH
Publication of EP4003896A1 publication Critical patent/EP4003896A1/de
Application granted granted Critical
Publication of EP4003896B1 publication Critical patent/EP4003896B1/de
Publication of EP4003896C0 publication Critical patent/EP4003896C0/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/04—Driving gear manually operated
    • B66D1/06—Safety cranks for preventing unwanted crank rotation and subsequent lowering of the loads
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D3/00—Portable or mobile lifting or hauling appliances
    • B66D3/12—Chain or like hand-operated tackles with or without power transmission gearing between operating member and lifting rope, chain or cable
    • B66D3/14—Chain or like hand-operated tackles with or without power transmission gearing between operating member and lifting rope, chain or cable lever operated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect
    • B66D5/14—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect embodying discs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/32—Detent devices
    • B66D5/34—Detent devices having latches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/05—Brakes with mechanisms with latches for hoists or similar devices

Definitions

  • the invention relates to a hoist, in particular a lever hoist, according to the features in the preamble of claim 1.
  • a hoist in particular a lever hoist, generally uses round steel chains as a means of carrying or pulling and is used for lifting, lowering and pulling loads.
  • the lifting movement can be generated by hand, compressed air or an electric motor.
  • the present invention relates to a manual lever hoist.
  • a lever-operated hoist which is also referred to as a pull hoist or chain hoist.
  • the hoist has a lifting hook as the upper fastening element and a load hook as the lower stop element.
  • the upper fastener and the lower stop member are a Housing indirectly connected.
  • the stop element is connected via a load chain as a traction means to a traction drive, which is located in the housing of the hoist.
  • the traction drive can be set in rotation within the housing by a pivoting movement of a hand lever.
  • the lever arm engages in a transmission device, which in turn is connected to the traction drive. In this way it is possible to move or tie down an object.
  • the traction mechanism includes a load pressure brake, a load chain wheel and a gear, with the gear often being designed as a planetary gear.
  • the hand lever and the ratchet mechanism's ratchet wheel are located at one end of a drive shaft which passes through the load pressure brake and the load sprocket.
  • the gearbox At the other end of the drive shaft is the gearbox, which is then connected to the load chain wheel in a torque-transmitting manner.
  • the load pressure brake consists of a ratchet wheel disc with recesses or teeth on its outer circumference, two friction elements on both sides of the ratchet wheel disc, usually friction discs or linings, and two pawls articulated on the housing, which are pressed against the ratchet wheel disc under the influence of ratchet springs .
  • the two friction elements enter into a frictional connection with the ratchet wheel disk and with a pressure disk or ratchet wheel fixed to the shaft.
  • the ratchet wheel is axially displaceable on a movement thread of the drive shaft.
  • the task of the load pressure brake is to keep the load carried by the hoist at the respective height or position when the ratchet wheel is stationary.
  • the ratchet wheel is then pressed against the thrust washer via the ratchet wheel disk and the integrated friction elements.
  • the pawls are located in the peripheral recesses of the ratchet disc. If the ratchet wheel is turned in the lifting direction, the pawls slide over the teeth of the ratchet wheel disc until the ratchet wheel comes to a standstill. Then the pawls snap back into the recesses of the ratchet disc.
  • the ratchet wheel When lowering the load, the ratchet wheel turns in the opposite direction rotated, causing it to slide axially on the motion threads of the drive shaft and breaking frictional contact with the friction elements of the ratchet wheel disc and thrust washer.
  • the load can drop until the rotating shaft compensates for the axial play again.
  • the drive or drive shaft can accelerate and rotate so quickly that the standard load pressure brake no longer engages because the pawls are inertial can no longer reach into the recesses of the ratchet wheel disc.
  • Such an exceptional situation albeit extremely rare, can arise, for example, when working at great heights on overhead lines. There is then a risk of the load chain rattling out. Such a situation can also occur when lowering against a jammed load chain. Even if the locking hooks of the load pressure brake are blocked due to extraordinary circumstances such as e.g. B. corrosion or ice formation are not free, it can lead to such an exceptional situation.
  • EP 0 279 144 B1 includes a safety brake for a driven shaft in the prior art.
  • This comprises a brake disc and a cam disc for a roller that can be pressed on it by a release spring, which causes a pawl to engage in a toothed ring arranged on the shaft when the shaft rotates excessively.
  • the EP 3 395 746 A1 In addition to the load pressure brake, proposes another safety device in the form of a safety brake, which uses the centrifugal force of centrifugal elements to limit the speed.
  • the invention is based on the object of demonstrating a safety and operationally improved hoist, in particular a lever hoist, in which an impermissible increase in the speed of the drive shaft is prevented.
  • a hoist in particular a lever hoist, comprises a housing in which a load chain wheel and a drive shaft driving the load chain wheel via a gear are rotatably mounted.
  • a drive, a load pressure brake and a safety brake are also provided.
  • a load chain can be moved via the load chain wheel.
  • the safety brake has a locking disc with locking teeth and a control disc with control cams and a catch hook.
  • the locking disk and the control disk can be rotated in relation to one another, with the rotation being limited by limiting the rotational travel.
  • the catch hook is arranged so that it can pivot.
  • the catch hook has two legs and has a catch contour at a front end and a tactile contour at a rear end.
  • the catch hook is assigned to the locking disk and the control disk in such a way that the tactile contour rests against the control disk, in particular the outer contour of the control disk, under the influence of a spring element and slides along it when the control disk rotates.
  • the pawl contour can be brought into locking engagement with a locking tooth of the locking disk.
  • the catch hook is guided with the tactile contour over the control disc and the pawl contour does not engage in the locking disc. If it is triggered when a defined speed is exceeded, the tactile contour of the catch hook lifts off the control disc or the control cam of the control disc and the pawl contour of the catch hook snaps into a ratchet tooth on the locking disc. This stops the locking disk, while the control disk arranged coaxially behind the locking disk continues to rotate along a predetermined twisting path of the rotary travel limitation until the twisting path is exhausted and the locking disk and the control disk lock against one another.
  • the rotational path limiter has at least one curved track and a stop body which can be displaced along the curved track. In the end position, i.e. after the torsional path between locking disk and control disk has been exhausted, the stop body comes to a locking stop at the end of the cam track.
  • the cam track is preferably formed by a slot.
  • the elongated hole is formed in the control disc.
  • a slot is preferably arcuate with a radius around the center of the control disc. It is particularly advantageous to provide a number of elongated holes offset from one another on a pitch circle in the control disk.
  • the cam track it is also possible for the cam track to be formed in a groove. This can be provided in the control disk or in the locking disk.
  • the stop body is preferably a pin.
  • the stop pin or pins are preferably fixed in the locking disk and protrude from it in the direction of the control disk, engaging in the slots.
  • a further embodiment provides that latching elements are integrated between the locking disk and the control disk. These fix the locking disk and the control disk in the initial position and in the end position.
  • the locking elements are preferably formed by balls.
  • the locking elements are held in recordings and interact with locking surfaces.
  • An advantageous embodiment provides that the receptacles are in the control disk and the locking surfaces are formed in the locking disk.
  • ratchet teeth are distributed evenly around the circumference of the ratchet disk.
  • control cams are distributed evenly on the circumference of the control disk.
  • the control cams are in particular formed by the contour of the control disk itself.
  • the control disc is preferably configured in a triangular shape with a rounded outer contour.
  • the control disk has a central socket with internal teeth. With the internal toothing, the control disk sits on a longitudinal section of the drive shaft that is provided with external toothing.
  • the control disc is positioned with a central bearing section on the central socket.
  • the locking disc is secured on the socket by securing elements.
  • An advantageous practical embodiment provides that in the starting position of the locking disk and the control disk, the rear outer contour of the locking teeth is aligned with the outer contour of the control disk.
  • the control disk covers the adjacent flat side of the locking disk.
  • the catch hook of the safety brake is pivotably mounted on a bolt on a side plate that can be integrated into the housing.
  • the spring element is preferably a torsion spring.
  • damping elements can be integrated between the locking disk and the control disk in order to dampen the braking effect in the event of an emergency stop.
  • the unlocking preferably comprises a locking slide which is designed to block the locking disc while the control disc connected to the drive shaft is rotated in the lifting direction (clockwise) until the two discs are again aligned in the starting position.
  • a backstop is provided, which reverse rotation of the locking disc and the Control disk prevented from returning to its original position.
  • the safety brake remains in the locked state.
  • One embodiment of the backstop provides that clamping rollers are positioned in recesses in the locking disk. These are arranged and designed in such a way that the locking disc and control disc cannot be reset to their original position.
  • the safety brake cannot be triggered unintentionally with this version, e.g. B. when pulling out by hand, the starting position is secured with a shear pin. Only when a certain threshold value is exceeded, depending on the speed and torque, does the shear pin shear off and the safety brake carries out the emergency braking.
  • the hoist according to the invention can be used in a wide variety of applications. It can be used in any application with reversing loads, for example in overhead line construction or for personal security.
  • the hoist is compact and lightweight.
  • the additional safety function via the safety brake is implemented with just a few parts.
  • the mechanism requires an active movement, so that if the spring is lost, the pawls of the load pressure brake get stuck, etc., the safety brake will be triggered.
  • the safety brake locks itself automatically. As a result, the catch hook always remains engaged, even if the load swings back.
  • the figures 1 and 2 show a hoist according to the invention in the form of a hand-operated lever hoist 1.
  • Part of the lever hoist 1 is a housing 2, which is composed of several housing parts 3, 4 and side plates 5, 6 and spacer frame 7.
  • the lever hoist 1 has a support hook 8 as the upper fastening element and a load hook 9 as the lower stop element.
  • the support hook 8 and the load hook 9 are connected to one another indirectly via the housing 2 .
  • the load hook 9 is attached to one end of a load chain 10 .
  • a chain end piece 11 is provided at the other end of the load chain 10 .
  • the load chain 10 can be moved via a traction drive.
  • the traction mechanism essentially comprises a drive 12 with a hand lever 13, a ratchet wheel 14 and a switchable ratchet mechanism 15, a load pressure brake 16, a load chain wheel 17 and a gear 18.
  • the hand lever 13 and the ratchet wheel 14 of the ratchet mechanism 15 sit at one end 19 of a Drive shaft 20, which passes through the load pressure brake 16 and the load chain wheel 17.
  • At the other end 21 of the drive shaft 20 is the gear 18, which is connected to the load chain wheel 17 in a torque-transmitting manner.
  • a hand wheel 22 is used to displace the ratchet wheel 14 axially on the drive shaft 20 in order to actuate a freewheel mechanism 23 of the lever block 1.
  • the load pressure brake 16 has a ratchet wheel disk 24 provided with teeth on its outer circumference.
  • the ratchet wheel disk 24 is provided with friction elements 25 in the form of friction linings on both sides.
  • the load pressure brake 16 has two pawls 26 which are pivotably mounted on the side plate 6 in the housing 2 and which are pressed onto the ratchet wheel disc 24 under the influence of ratchet springs 27 .
  • the load pressure brake 16 includes a thrust washer 28 on which the ratchet wheel disk 24 is mounted.
  • the ratchet wheel 14 can be displaced axially on a movement thread 29 of the drive shaft 20 .
  • the figure 3 shows the lever hoist 1 with the ratchet wheel 14, hand lever 13 and hand wheel 22 dismantled.
  • the load pressure brake 16 has the task of holding the load carried by the lever block 1 when the ratchet wheel 14 is stationary.
  • the ratchet wheel 14 is then pressed against the pressure disk 28 via the ratchet wheel disk 24 and the integrated friction elements 25 .
  • the pawls 26 are in the circumferential recesses of the ratchet wheel 24. If the ratchet wheel 14 in the lifting direction rotated, the pawls 26 slide over the teeth of the ratchet wheel disc 24 until the ratchet wheel 14 comes to a standstill. The pawls 26 then snap back into the recess of the ratchet wheel disk 24.
  • the ratchet wheel 14 When the load is lowered, the ratchet wheel 14 is rotated in the opposite direction, causing it to slide axially on the motion thread 29 of the drive shaft 20 and the frictional contact with the friction elements 25 of the ratchet wheel disk 24 and the Thrust washer 28 is repealed. The load can then be lowered until the after-rotating drive shaft 20 compensates for the axial play again.
  • the lever hoist 1 has a safety brake 30, 31.
  • the safety brake 30, 31 has the task of carrying out emergency braking in extreme situations in which the speed of the drive shaft 20 can be so high that the load pressure brake 16 no longer engages due to inertia.
  • a safety brake 30 and its operation are with reference to the Figures 4 to 17 described.
  • a second embodiment of a safety brake 31 is based on the Figures 18 to 23 explained. Parts or parts that correspond to one another are provided with the same reference symbols.
  • the safety brake 30, 31 is arranged coaxially below or behind the load pressure brake 16 in the direction of the load chain wheel 17.
  • the safety brake 30, 31 has a locking disk 32 with locking teeth 33 and a control disk 34 with control cams 35 and a catch hook 36. On the circumference of the locking disk 32 are several, three in the embodiment, ratchet teeth 33 are evenly distributed.
  • the control disk 34 has a triangular configuration with control cams 35 rounded on its circumference.
  • the control disk 34 has a central socket 38 provided with internal teeth 37, on which the locking disk 32 is positioned with a central bearing section 39 and secured in position by securing elements 40, 41.
  • the control disk 34 and the locking disk 32 with the control disk 34 are held on a threaded section 43 of the drive shaft 20 provided with external teeth 42 via the connecting piece 38 and the internal toothing 37 .
  • the catch hook 36 is pivotably arranged on the side plate 5 of the lever hoist 1 .
  • a spring element 44 in the form of a torsion spring
  • the catch hook 36 is mounted on a bolt 45 on the side plate 5 and secured by a retaining ring 46 .
  • the mounting of the catch hook 36 on the bolt 45 is in the central length region of the catch hook 36, so that the catch hook 36 is mounted like a rocker.
  • the locking disk 32 and the control disk 34 can be rotated in opposite directions.
  • the rotation of locking disk 32 and control disk 34 relative to one another is limited by a limiter 47 of rotational travel.
  • the rotary travel limiter 47 includes a cam track 48 which is formed in a slot 49 in the shape of a segment of a circular arc in the control disk 34 .
  • a stop body 50 in the form of a pin can be displaced along the cam track 48 . It can be seen that three elongated holes 49 are arranged in the control disk 34 in an evenly offset manner on a pitch circle. Correspondingly, three pins are incorporated as stop bodies 50 in assembly openings 51 of locking disk 32 .
  • the stop bodies 50 protrude in the direction of the control disk 34 opposite the locking disk 32 and engage in the elongated holes 49.
  • the rotary travel limiter 47 allows the locking disk 32 to be rotated by 45° relative to the control disk 34 .
  • Locking elements 52 in the form of steel balls are integrated between the locking disk 32 and the control disk 34 .
  • the latching elements 52 fix the locking disk 32 and the control disk 34 in the initial position and in the end position after rotation.
  • the latching elements 52 are held in receptacles 53 in the control disk 34 and contact latching surfaces 54 in the shape of a segment of a sphere in the locking disk 32 and interact with them in a counteracting and movement-inhibiting manner.
  • the catch hook 36 has a catch contour 56 at a front end 55 .
  • the pawl contour 56 has a pointed catch tooth 57 with a front catch flank 58 which is configured to a front locking flank 59 of a locking tooth 33 of the locking disk 32 is adapted.
  • a tactile contour 61 is formed on the catch hook 36 at the rear end 60 .
  • the rear end 60 of the catch hook 36 is rounded.
  • the spring element 44 causes the pawl contour 56 to lie outside the outer circumference of the locking disk 32 during normal operation. In normal operation, the catch hook 36 slides with the rear tactile contour 61 along the control disc 34.
  • the front pawl contour 56 is raised.
  • the feeler contour 61 of the catch hook 36 lifts off the control disc 34 or the control cam 35 as a result of the mass inertia and the acting acceleration forces.
  • the catch hook 36 tilts and rotates about the bolt 35 in the locking disc 32.
  • the pawl contour 56 of the catch hook 36 beaks into a locking tooth 33 of the locking disc 32 and comes there with the catch edge 58 on the locking edge 59 to the system.
  • the locking disk 32 is stopped, while the control disk 34 arranged coaxially behind it continues to rotate along the predetermined rotational path of the rotational path limiter 47 .
  • the twisting takes place until the stop bodies 50 come to a stop at the end 62 of the elongated holes 49 located in the direction of rotation.
  • the locking disk 32 and the control disk 34 are then blocked against each other. In this way, a form-fitting connection between the drive shaft 20 and the lever block 1 is established. Further spinning of the load chain wheel 17 and rustling of the load chain 10 is prevented.
  • the figure 11 shows a normal situation of load pressure brake 16 and safety brake 30.
  • the pawls 26 engage in the ratchet wheel disc 24 and hold the load.
  • figure 12 indicates a problem situation.
  • the pawls 26 of the load pressure brake 16 are not free.
  • the pawls 26 do not engage the ratchet disc 24 .
  • a load cannot be held.
  • a dangerous excessive increase in speed can occur in the opposite direction to the pulling direction of the lever hoist 1, combined with the load chain 10 rattling out.
  • the Figures 13 and 14 show the safety brake 30 in a normal situation or starting position.
  • the locking disk 32 and the control disk 34 are aligned such that the rear outer contour of the locking teeth 33 coincides with the outer contour of the control disk 32.
  • the tactile contour 61 of the catch hook 36 is pressed against the outer contour of the control disk 34 by the spring force of the torsion spring and slides along the control cam 35.
  • the tactile contour 61 lies both at the top dead center of the control disk 34 ( figure 13 ) as well as in the bottom dead center of the control disc 34 ( figure 14 ) on a control cam 35.
  • the front pawl contour 56 of the catch hook 36 is lifted out of the effective range of the locking disk 32 and its locking teeth 33.
  • the tactile contour 61 of the catch hook 36 is accelerated outwards and lifts off the control disk 34.
  • the front catch tooth 57 of the pawl contour 56 snaps into the locking disc 32 (see Fig figure 15 ) and comes to rest with its front catch flank 58 blocking on the locking flank 59 of a locking tooth 33 (see figure 16 ).
  • the control disk 34 driven by the load, continues to rotate 45° counterclockwise (arrow P1) and thereby locks the ratchet wheel 14. This effect is self-reinforcing, i.e. the catch hook 36 falls in the deeper the stronger the tactile contour 61 is raised on the opposite side by the control disc 34.
  • an unlocking device 63 is provided.
  • This comprises a slider 64 for actuating the unlocking device 63 and a blocking body 66 which is under the influence of a tension spring 65.
  • actuating the slider 64 (arrow P2), it blocks the blocking disk 32 with the blocking body 66 and holds it in place, so that the blocking disk 32 is prevented from rotating while the control disk 34 is actuated in the lifting direction (clockwise) (arrow P3) via the handwheel 22 or the hand lever 13. In this way, the locking disk 32 and the control disk 34 are displaced relative to one another and brought into their aligned initial position.
  • the Figures 18 to 23 show a second embodiment of a safety brake 31. As previously described, this has a locking disc 32 with locking teeth 33 and a control disc 34 with locking cams 35 and one in the Figures 18 to 23 fishing hook not shown. The catch hook corresponds to the previous explanation. The same applies to the rotation limit and the function of the safety brake 31.
  • a backstop 67 is provided for the safety brake 31 .
  • the backstop 67 prevents the locking disk 32 and control disk 34 from rotating into their starting position after the safety brake 31 has been triggered, ie is in its blocked state.
  • the backstop 67 has recesses 68 in the locking disk 32 which are offset on a pitch circle. Pinch rollers 69 are accommodated there.
  • the rear wall 70 of a pocket-shaped recess 68 runs obliquely, so that the recess 68 tapers counterclockwise. This creates a wedge effect between the locking disk 32 and the control disk 34 via the clamping rollers 69, so that the backstop 67 prevents the locking disk 32 and the control disk 34 from rotating relative to one another by friction.
  • a shear pin 71 is integrated into the safety brake 31.
  • the shear pin 71 is driven through a mounting hole 72 in the locking disk 32 into a mounting hole 73 in the control disk 34 .
  • the shear pin 71 prevents the safety brake 31 from being triggered unintentionally, for example when it is pulled out by hand.
  • the shear pin 71 secures the safety brake 31 in the starting position. Only when a certain threshold value is exceeded when the safety brake 31 is blocked is the shear pin 71 sheared off and the safety brake 31 can effect emergency braking.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Retarders (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
EP20708417.9A 2019-07-24 2020-02-13 Hebezeug Active EP4003896B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019120036.9A DE102019120036A1 (de) 2019-07-24 2019-07-24 Hebezeug
PCT/DE2020/100101 WO2021013286A1 (de) 2019-07-24 2020-02-13 Hebezeug

Publications (3)

Publication Number Publication Date
EP4003896A1 EP4003896A1 (de) 2022-06-01
EP4003896B1 true EP4003896B1 (de) 2023-06-28
EP4003896C0 EP4003896C0 (de) 2023-06-28

Family

ID=69740073

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20708417.9A Active EP4003896B1 (de) 2019-07-24 2020-02-13 Hebezeug
EP20710033.0A Active EP4003897B1 (de) 2019-07-24 2020-02-13 Hebezeug

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP20710033.0A Active EP4003897B1 (de) 2019-07-24 2020-02-13 Hebezeug

Country Status (11)

Country Link
US (2) US11999600B2 (pl)
EP (2) EP4003896B1 (pl)
JP (2) JP7295331B2 (pl)
CN (2) CN114174210B (pl)
AT (2) AT17647U1 (pl)
CA (2) CA3146206A1 (pl)
DE (3) DE102019120036A1 (pl)
ES (2) ES2952196T3 (pl)
PL (2) PL4003897T3 (pl)
WO (2) WO2021013286A1 (pl)
ZA (2) ZA202200895B (pl)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019120036A1 (de) 2019-07-24 2021-01-28 Columbus Mckinnon Industrial Products Gmbh Hebezeug
US20240059533A1 (en) * 2020-12-17 2024-02-22 Columbus Mckinnon Industrial Products Gmbh Lever hoist
CN113071720B (zh) * 2021-03-24 2022-08-30 哈尔滨工业大学 一种工具包转移绳索缓释装置
CN116161577B (zh) * 2023-03-06 2025-10-28 中山市罗顿智能科技有限公司 顶升机及其控制方法

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CA3164748C (en) 2024-11-05
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CA3153687A1 (en) 2021-01-28
AT17646U1 (de) 2022-10-15
CA3146206A1 (en) 2021-01-28
EP4003897A1 (de) 2022-06-01
DE202020106349U1 (de) 2020-11-23
WO2021013285A1 (de) 2021-01-28
EP4003896A1 (de) 2022-06-01
US12006190B2 (en) 2024-06-11
ZA202200895B (en) 2023-09-27
ES2952011T3 (es) 2023-10-26
JP2022542244A (ja) 2022-09-30
CN114174210A (zh) 2022-03-11
DE102019120036A1 (de) 2021-01-28
PL4003896T3 (pl) 2023-10-02
EP4003897C0 (de) 2023-06-28
JP2022542856A (ja) 2022-10-07
US11999600B2 (en) 2024-06-04
PL4003897T3 (pl) 2023-10-09
CN114174210B (zh) 2023-06-23
CN114174211A (zh) 2022-03-11
US20220274813A1 (en) 2022-09-01
JP7232378B2 (ja) 2023-03-02
EP4003897B1 (de) 2023-06-28
EP4003896C0 (de) 2023-06-28
US20220242704A1 (en) 2022-08-04
ES2952196T3 (es) 2023-10-30
DE202020106350U1 (de) 2020-11-23
JP7295331B2 (ja) 2023-06-20
ZA202200896B (en) 2023-06-28
CA3164748A1 (en) 2021-01-28

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