WO2020148174A1 - Entraînement pour une porte-tambour rotative - Google Patents

Entraînement pour une porte-tambour rotative Download PDF

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Publication number
WO2020148174A1
WO2020148174A1 PCT/EP2020/050497 EP2020050497W WO2020148174A1 WO 2020148174 A1 WO2020148174 A1 WO 2020148174A1 EP 2020050497 W EP2020050497 W EP 2020050497W WO 2020148174 A1 WO2020148174 A1 WO 2020148174A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
stage
drive
unit
worm
Prior art date
Application number
PCT/EP2020/050497
Other languages
German (de)
English (en)
Inventor
Roland Vögele
Original Assignee
Geze 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 Geze Gmbh filed Critical Geze Gmbh
Priority to EP20700476.3A priority Critical patent/EP3912258A1/fr
Priority to CN202080009545.2A priority patent/CN113302821A/zh
Publication of WO2020148174A1 publication Critical patent/WO2020148174A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
    • H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
    • H02K2213/03—Machines characterised by numerical values, ranges, mathematical expressions or similar information
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K29/00—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices

Definitions

  • the invention relates to a drive for a revolving door with an electric drive unit and a gear unit comprising a gear motor. It also relates to a revolving door system with such a drive.
  • Revolving revolving door systems generally comprise a revolving revolving door with several revolving revolving door wings that can be rotated together around a central axis, as well as a geared motor assigned to the revolving revolving door with an electric drive unit and a transmission unit that follows a chain step.
  • the revolving revolving door cover requires a height of at least 150 mm.
  • the revolving revolving door drives that were previously common are difficult to brake.
  • the four-stage gearboxes previously used for revolving revolving doors are not only very heavy and large, they are also relatively expensive to manufacture.
  • Relatively flat revolving door multi-pole motors are known. However, these are also relatively heavy and expensive, which is particularly due to the many large copper coils that are required to generate the high torque without Ge gearboxes.
  • no electrically actuable brake with brake linings is provided or can be implemented in these known multipole motors.
  • the invention has for its object to provide a drive for a revolving door and a revolving door system of the type mentioned, in which the aforementioned disadvantages are eliminated.
  • the drive should in particular have a more compact design and in particular have a lower height and be able to be braked significantly more quickly during operation. In particular, this should also enable significantly smaller heights of the ceilings of the revolving revolving doors that accommodate the drives.
  • this object is achieved by a drive with the features of claim 1 and a revolving door system with the features of claim 21.
  • Preferred embodiments of the drive according to the invention and the revolving revolving door system according to the invention result from the subclaims.
  • the drive according to the invention for a revolving door comprises a gear motor with an electric drive unit and a gear unit, the electric drive unit comprising a brushless DC motor and the gear unit being designed in several stages and provided with a gear, in particular with an angular gear and at least one spur gear stage.
  • a brushless DC motor also known as a BLDC motor (brushless direct current motor) or an EC motor (electronically commutated motor), is not based on the principle of operation of the DC machine, contrary to the name, but is constructed like a three-phase synchronous machine with excitation by Permanent magnets.
  • the multi-strand, for example three-strand, three-phase winding is controlled by electronics so that it generates a rotating magnetic field that pulls the permanent magnet excited rotor.
  • the drive is not only more compact, in particular having a smaller flea.
  • the drive can also be braked significantly faster during operation. Due to the more compact design and in particular smaller fleas, significantly smaller fleas of the ceilings of the revolving doors in question which accommodate the drives are also possible.
  • the ceiling height can be reduced from 160 mm to less than 80 mm.
  • the chain step previously required is no longer required. Instead, the drive with its output shaft can plunge directly into the drive shaft of the revolving door connected to the revolving door leaves. It will also achieve better efficiency.
  • the required nominal power is achieved with the thinner brushless DC motor by the higher compared to a conventional asynchronous motor. here speed and better efficiency achieved.
  • the geared motor is also easier to install than before.
  • the elimination of parts also further reduces costs.
  • the multi-stage gear unit with an angular gear and spur gear stages is not only smaller, but also correspondingly cheaper.
  • the gear unit also has less play than a conventional gear unit or a gear unit with a chain, which shortens the braking distance in the event of an emergency stop.
  • the geared motor advantageously has a height of ⁇ 160 mm, in particular ⁇ 120 mm and preferably ⁇ 80 mm.
  • the electric drive unit is provided with a braking device.
  • the electric drive unit is preferably arranged with its longitudinal axis parallel to the axis of its armature shaft at an angle of approximately 90 ° to a center plane containing the mutually parallel, successive gear axes of the multi-stage gear unit.
  • the gear unit following the electric drive unit, comprises an angular gear with a worm gear with a worm and a worm gear meshing therewith, a helical-toothed spur gear stage and a straight-toothed spur gear stage.
  • the helical-toothed spur gear stage comprises a pinion with non-rotatably connected to the worm gear of the worm stage with in particular eight or fewer than eight teeth and a meshing gear and / or the spur-toothed spur gear stage includes a sprocket non-rotatably connected to the gear of the helically toothed spur gear stage and a sprocket Comb the gear wheel, which is connected in a rotationally fixed manner to an output shaft.
  • the pinion rotatably connected to the gear of the helically toothed spur gear stage is welded to the gear of the helically toothed spur gear stage and / or the gear which is non-rotatably connected to the output shaft is welded to the output shaft.
  • the multi-stage gear unit is preferably designed such that it survives 300,000 emergency stops in accordance with DIN 18 650 with a drive torque of approximately 1000 Nm without damage.
  • the pinion of the helical spur gear stage is connected to the worm gear of the worm stage by an interference fit or by brazing and / or the pinion of the spur gear stage with the gear wheel of the helical spur gear stage and the gear of the spur gear stage the output shaft each connected by brazing.
  • Brazing is particularly advantageous to the extent that, with a short press fit of the respective pinion or wheel, the maximum torque of, for example, 1000 Nm can be transmitted without problems to the output shaft.
  • the helical spur gear stage or its pinion and / or the straight-toothed spur gear stage or its pinion can each be mounted in the transmission housing via roller bearings, in particular ball bearings.
  • the components of the multi-stage gear unit can be mounted in a gear housing made of, in particular, cast and machined aluminum and in a housing cover.
  • a cross section in particular a triangular shaped seal, in particular a rubber shaped seal, can expediently be provided between the transmission housing and the housing cover.
  • at the fitting of the electrical drive unit to the gear unit or in the gear housing at least one sealing ring combined with a shaft sealing ring can be provided which ensures the oil tightness towards the gear housing with an O-ring and at the same time the motor or the electric drive unit for the gear housing bore centered.
  • At least one sealed needle bearing is expediently provided, which comprises a needle sleeve with at least one associated elastic seal and an axial needle ring.
  • the elastic seal prevents the lubricant from escaping. If, instead of the sealed needle bearing preferred according to the invention, a second ball bearing were used, either the center distance would have to be increased and an intermediate wheel used, or a higher-construction gear would have to be accepted. Due to the sealed needle bearing provided according to the invention, the transmission unity, on the other hand, without offering greater drive torques on the output shaft, can be kept correspondingly smaller and manufactured more cost-effectively.
  • a further preferred practical embodiment of the drive according to the invention is characterized in that a roller or ball bearing assigned to the output shaft is partially in an axial recess in the rotationally fixedly connected to the drive shaft from the gear wheel of the straight-toothed spur gear stage and / or one of the straight-toothed spur gear stage or their Rolling or ball bearing assigned to the pinion is immersed in an axial recess in the gear of the helical toothed spur gear stage which is connected in a rotationally fixed manner to this pinion.
  • the axial recesses of the gearwheels also contribute significantly to the desired minimum height of the transmission unit.
  • the drive becomes particularly compact in construction, and in particular its height is further minimized by such an embodiment.
  • the electric drive unit has a nominal speed in the range of 3000 rpm and / or has a diameter of ⁇ 100 mm or ⁇ 80 mm or ⁇ 63 mm.
  • “in the range of 3000 1 / min” is to be understood in particular “3000 1 / min ⁇ 30%”.
  • an asynchronous motor commonly used up to now has a nominal speed of 1500 rpm and a diameter of 122 mm.
  • the service life of both motors is mainly determined by the ball bearings and is essentially the same.
  • the required nominal power in the significantly thinner brushless DC motor used according to the invention is achieved by the higher speed and the better efficiency.
  • the multi-stage gear unit expediently has a transmission ratio> 500, in particular> 550 and preferably> 600.
  • the worm stage has a transmission ratio in the range of 10 and / or comprises a worm, in particular made of steel, which is pressed onto the armature shaft of the electric drive unit and has in particular three teeth. “In the range of 10” is to be understood in particular as “10 ⁇ 30%”.
  • the worm wheel of the worm stage consists entirely or preferably at least partially of bronze and / or brass, with which a higher strength and wear resistance compared to plastic is achieved.
  • the helical-toothed spur gear stage of the multi-stage gear unit comprises a pinion with eight or less than eight teeth, in particular a 5-tooth sprocket, and a 61-toothed gear wheel meshing with it and / or the spur gear spur gear an 8-tooth pinion and a 41-tooth gear meshing with it.
  • the straight-toothed spur gear stage of the multi-stage gear unit has a transmission ratio of approximately 5.125 and / or the module of the toothing of the straight-toothed spur gear stage of the three-stage gear unit is in the range of 3 mm. "In the range of 3 mm” is to be understood in particular as “3 mm ⁇ 35%”.
  • the helical gear stage preferred according to the invention is the most compact form imaginable.
  • the output shaft of the multi-stage gear unit is preferably provided with a through hole for its coupling to the revolving revolving door with a square and / or for receiving in particular the monitoring of the revolving revolving door wing cable.
  • the multi-stage gear unit is designed in three stages, wherein it preferably includes a worm stage with a worm and a worm wheel meshing with it, a helical spur gear stage and a spur gear spur gear stage.
  • the armature shaft of the electric drive unit can be in particular triple roller bearings in the drive unit, wherein it can be mounted, for example, by a further or third bearing with, in particular, greater play than in the roller bearings in the transmission housing.
  • a further bearing with a large amount of play in the transmission housing, excessive bending of the armature shaft in the event of a brief overload, such as an emergency stop, is avoided.
  • the revolving revolving door system comprises a revolving revolving door with a plurality of revolving revolving door leaves which are connected to a central drive shaft and can be rotated about this around a central axis of rotation. It is characterized in that it comprises a drive according to the invention assigned to the revolving door.
  • the drive shaft of the revolving door connected to the revolving door leaves extends along the central axis of rotation.
  • the revolving revolving door system also includes electronics for controlling the drive and a power supply unit for supplying the drive and the electronics, the drive, the electronics and the power supply unit preferably being accommodated in a center ring of a revolving revolving door cover.
  • the center ring can not only have a smaller diameter of about 0.9 m, but also in particular a reduced height ⁇ 80 mm, whereby it preferably has a height of ⁇ 75 mm.
  • the space required for such a center ring of the revolving revolving door cover is thus considerably reduced by the education according to the invention.
  • the ceiling height of revolving revolving doors can be reduced from at least 160 mm to less than 80 mm from the values previously required, inter alia, because of the subsequent chain step.
  • the ceiling height of a revolving revolving door can therefore be reduced by more than 80 mm.
  • All drive parts have space in a center ring, now around 0.9 m in diameter. A glass ceiling is also possible outside the ring.
  • the geared motor according to the invention is significantly smaller and lighter due to the rapidly rotating brushless direct current or BLDC motor (brushless direct cur rent) and the gearbox with only three stages. It is easier to assemble.
  • the helical-toothed spur gear stage has a high gear ratio, while the straight-toothed spur gear stage with the needle bearing comprising the needle sleeve and the axial needle bearing is extremely compact in terms of the transferable, relatively high torques.
  • a gear ratio of 625 now only requires three gear stages.
  • the Geretege housing with gear cover is relatively simple in its construction and therefore inexpensive. With low noise of the drive according to the invention, good efficiency is achieved.
  • the drive according to the invention can also be used as an underfloor drive.
  • the three gear stages according to the invention provide less gear backlash than four gear stages, which leads to a shorter braking distance in the event of an emergency stop, since the time is shorter in which the drive tooth flank is switched to the braking tooth flank.
  • the emergency stop function is mandatory.
  • it is also possible to reduce the braking torque with the same braking distance since the gear backlash in the drive according to the invention is only three quarters of a four-stage gearbox and the braking time can thus be extended in the deceleration.
  • a glass ceiling is possible outside the center ring.
  • Significant cost savings per drive are achieved. Due to the fast rotating brushless DC motor or BLCD motor and the gear unit with in particular only three stages, the drive according to the invention is smaller and lighter, the worm stage making the gearbox quiet, the helical spur gear stage bringing a high gear ratio and the straight-toothed spur gear stage together with the needle sleeve and the axial needle bearing measured in terms of the transmissible torques.
  • the gear housing with gear cover is relatively simple and inexpensive to manufacture. With a quieter mode of operation, good efficiency is achieved.
  • the drive according to the invention can also be used as an underfloor drive.
  • FIG. 1 is a schematic perspective view of an exemplary embodiment of a revolving door system for which a drive according to the invention is used
  • FIG. 2 is a schematic perspective view of an exemplary embodiment of a drive according to the invention from below,
  • FIG. 3 is a schematic cross-sectional view of the drive according to FIG. 2,
  • Fig. 4 is a schematic sectional view of the drive according to
  • Fig. 5 is a schematic exploded view of the
  • FIG. 1 shows the basic structure of an exemplary revolving door system 10 in which a drive 12 according to the invention is used.
  • the revolving revolving door system 10 comprises a revolving revolving door 14 with a plurality of revolving revolving door leaves 18 which are connected to a drive shaft 16 and can be rotated together about a central axis of rotation, and a ceiling 20 which provides a receiving space for the various components of the drive 12 and has a height H.
  • the drive shaft 16 connected to the revolving door leaves 18 of the revolving door leaves 18 can be driven or rotated and braked via the drive 12.
  • the drive 12 according to the invention shown in more detail in FIGS. 2 to 5 comprises a geared motor 22, 24 with an electric drive unit 22 and a gear unit 24.
  • BLDC brushless direct current
  • the gear unit 24 is designed, for example, in three stages.
  • the electrical drive unit 22 with its longitudinal axis parallel to the axis 30 of its armature shaft 28 is at an angle of approximately 90 ° to one of the mutually parallel transmission axes 32, 34, 36 of the three-stage transmission unit 24 containing th 38 arranged.
  • the gear unit 24 comprises, starting from the electric drive unit 22, successively an angular gear 40 with a worm or screw gear stage 40 'with a worm 42 and one with this meshing worm gear 44, a helical gear stage 46 and a spur gear 48.
  • the helical-toothed spur gear stage 46 comprises a pinion 50, which is non-rotatably connected to the worm gear 44 of the worm stage 40 ', and a gear 52 meshing with it.
  • the straight-toothed spur gear stage 48 comprises a pinion 54 which is non-rotatably connected to the gear 52 of the helical-toothed spur gear stage 47 and a gear 58 which meshes with it and is non-rotatably connected to an output shaft 56.
  • the pinion 50 of the helical gear stage 46 can be connected to the worm wheel 44 of the worm stage 40, in particular by brazing or an interference fit.
  • the pinion 54 of the straight-toothed spur gear stage 48 can be connected to the gear 52 of the helical-toothed spur gear stage 48 and the gear 38 can be connected to the output shaft 56 by such brazing.
  • the helical spur gear stage 46 or its pinion 50 fixedly connected to the worm gear 44 and the straight-toothed spur gear stage 48 or its sprocket 54 non-rotatably connected to the gear 52 can each have rolling bearings, in particular ball or roller bearings, in a gear housing 60 orderly housing cover 62 may be mounted.
  • the remaining components of the three-stage gear unit 24 can also be mounted in the gear housing 60 with the associated housing cover 62.
  • This gear housing 60 can at least partially consist in particular of cast and machined aluminum.
  • a triangular shaped seal 64 in particular a rubber shaped seal, can be seen between the gear housing 60 and the housing cover 62, in particular (see FIG. 3 in particular).
  • At least one of the electric drive unit 22 in the gear unit 24 or in the gear housing 60 can be provided with a combined sealing ring 66 with a sealed ring, in the present case, for example, a combined with a shaft seal 66 Metal ring 68 is provided.
  • the output shaft 56 of the three-stage gear unit 24 is mounted in the gear housing 60 via a sealed roller bearing 72 combined with a shaft sealing ring 70, in the present case, for example, a ball bearing, and a further sealed bearing 74, in the present case, for example, a sealed needle bearing (cf. in particular Fig. 3).
  • the sealed needle bearing 74 provided for mounting the output shaft 56 comprises a needle sleeve 76 with at least one associated elastic seal and an axial needle ring 78.
  • the roller or ball bearing 72 assigned to the output shaft 56 is partially immersed in an axial recess 80 of the gear 58 of the straight-toothed spur gear stage 48, which is non-rotatably connected to the output shaft 56.
  • a roller bearing assigned to the straight-toothed spur gear stage 48 or its pinion 54 in the present case ball bearing 82, plunges into an axial recess 84 of the gear 52 of the helical-toothed spur gear stage 46 that is non-rotatably connected to this pinion 54.
  • the electric drive unit 22 can, for example, have a nominal speed in the range of 3000 rpm and / or have a diameter of ⁇ 100 mm or ⁇ 80 mm or ⁇ 63 mm. As already mentioned, "in the range of 3000 1 / min” is to be understood in particular as “3000 1 / m ⁇ 30%".
  • the three-stage gear unit in the present case can have a transmission ratio> 500, in particular> 550 and preferably> 600.
  • the worm stage 40 can in particular have a transmission ratio in the range of 10, wherein, as already mentioned, “in the range of 10” is to be understood in particular as “10 ⁇ 30%”.
  • the screw 42 for example made of steel, has three teeth in the present case and can in particular be pressed onto the armature shaft 28.
  • the armature shaft 40 of the electric drive unit 22 is mounted in the drive unit 22 in particular in two roller bearings and in the present case by a further bearing 86 (cf. in particular FIG. 4) with in particular greater play than in the roller bearings in the gear housing 60.
  • the worm wheel 44 of the worm stage 40 ′ can consist entirely or at least partially of bronze and / or brass.
  • the helical gear stage 46 of the multi-stage gear unit 24 in the present case comprises a pinion 50 with, for example, fewer than eight teeth, in the present case in particular a 5-toothed pinion 50, and a 61-toothed gear 52 meshing with it.
  • the straight-toothed spur gear stage 48 comprises in the present case, for example, an 8-tooth pinion 54 and a 41-tooth gear 58 meshing with it.
  • the straight-toothed spur gear stage 48 of the multi-stage gear unit 24 can in particular have a transmission ratio of approximately 5.125.
  • the module of the gear voltage of the straight-toothed spur gear stage 58 of the three-stage gear unit 24 can in particular be in the range of 3 mm.
  • “approximately 5.125” is to be understood in particular to be 5.125 ⁇ 5% ”and“ in the range of 3 mm ”is to be understood in particular to be“ 3 mm ⁇ 35% ”.
  • the output shaft 56 of the multi-stage gear unit 24 for coupling it to the revolving door 14 or its central drive shaft 16 can be provided with a square 88.
  • the output shaft 56 of the three-stage gear unit 24 can be provided with a through hole 90 for receiving cables, in particular for monitoring the revolving revolving door leaves 18.
  • the revolving revolving door system 10 can also include electronics for controlling the drive 12 and a power supply unit for supplying the drive 12 and the electronics.
  • the drive 10, the electronics and the power supply unit can in particular be accommodated in a center ring of the revolving door cover 20, which can have a diameter of approximately 0.9 m and a flea ⁇ 80 mm, in particular due to the compact design of the drive 12 according to the invention in the present case it has a flea of approximately 75 mm.
  • “about 0.9 m” is to be understood in particular as “0.9 m ⁇ 5%” and “about 75 mm” in particular as “75 mm ⁇ 10%”.
  • the drive according to the invention is characterized in particular by its compact design.
  • the drive or geared motor is hardly larger than an A4 sheet.
  • the only three-stage gear works very quietly, which is an additional advantage of the construction according to the invention.
  • the brake device attached to the electric drive unit enables the revolving door to be stopped very quickly, with braking being favored by the only three-stage gear unit. Thus, the game between the gears is less.
  • Due to the design of the drive 12 according to the invention the fleas Fl of the ceiling 20 of the revolving door 14 can be from 160 mm to less than 80 mm can be reduced.
  • the advantages already mentioned at the outset result with the drive according to the invention.
  • roller bearings 82 roller bearings, ball bearings 84 axial recess

Abstract

L'invention concerne un entraînement pour une porte-tambour rotative, l'entraînement comprenant un motoréducteur pourvu d'une unité d'entraînement électrique et d'une unité de transmission. L'unité d'entraînement électrique comprend un moteur à courant continu sans balais. L'unité de transmission est à étages multiples et est pourvue d'un engrenage d'angle et d'étages de roue dentée cylindrique.
PCT/EP2020/050497 2019-01-18 2020-01-10 Entraînement pour une porte-tambour rotative WO2020148174A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20700476.3A EP3912258A1 (fr) 2019-01-18 2020-01-10 Entraînement pour une porte-tambour rotative
CN202080009545.2A CN113302821A (zh) 2019-01-18 2020-01-10 用于旋转门的驱动装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019200656.6 2019-01-18
DE102019200656.6A DE102019200656A1 (de) 2019-01-18 2019-01-18 Antrieb für eine karusselldrehtür

Publications (1)

Publication Number Publication Date
WO2020148174A1 true WO2020148174A1 (fr) 2020-07-23

Family

ID=69157866

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/050497 WO2020148174A1 (fr) 2019-01-18 2020-01-10 Entraînement pour une porte-tambour rotative

Country Status (4)

Country Link
EP (1) EP3912258A1 (fr)
CN (1) CN113302821A (fr)
DE (1) DE102019200656A1 (fr)
WO (1) WO2020148174A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4341165A (en) * 1980-05-29 1982-07-27 Calandritti R Security system including a revolving door
EP0331770A1 (fr) * 1988-03-08 1989-09-13 Malkmus-Dörnemann, Carola, Dr. Tourniquet
US5773943A (en) * 1994-08-25 1998-06-30 Dorma Gmbh & Co. Kg Drive device for a revolving door
CN206942463U (zh) * 2017-06-14 2018-01-30 东龙顺（北京）科贸有限公司 一种助动水晶门

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000337456A (ja) * 1999-05-24 2000-12-05 Hitachi Ltd 歯車装置
DE10353366B3 (de) * 2003-11-14 2004-11-18 Magnetic Autocontrol Gmbh Antriebsvorrichtung für Durchgangs- oder Durchfahrtssperren und Tür- oder Torantriebe
EP2017423A1 (fr) * 2007-07-20 2009-01-21 Sesamo S.r.l. Système automatique pour portes battantes
DE102007062515C5 (de) * 2007-12-20 2020-06-25 Geze Gmbh Automatische Karusselltüranlage und Verfahren zumBetrieb einer automatischen Karusselltüranlage
DE102012110914B4 (de) * 2012-08-10 2016-02-25 Hörmann KG Antriebstechnik Bausatz zum Herstellen eines Drehflügeltür-Türantriebs sowie Herstellverfahren
DE102016106702B3 (de) * 2016-04-12 2017-08-10 Hörmann KG Antriebstechnik Getriebemotor für einen Gebäudeabschlussantrieb sowie damit versehener Gebäudeabschlussantrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4341165A (en) * 1980-05-29 1982-07-27 Calandritti R Security system including a revolving door
EP0331770A1 (fr) * 1988-03-08 1989-09-13 Malkmus-Dörnemann, Carola, Dr. Tourniquet
US5773943A (en) * 1994-08-25 1998-06-30 Dorma Gmbh & Co. Kg Drive device for a revolving door
CN206942463U (zh) * 2017-06-14 2018-01-30 东龙顺（北京）科贸有限公司 一种助动水晶门

Also Published As

Publication number Publication date
EP3912258A1 (fr) 2021-11-24
DE102019200656A1 (de) 2020-07-23
CN113302821A (zh) 2021-08-24

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