EP2639194B1 - Ascenseur à poulie motrice sans local de machine. - Google Patents

Ascenseur à poulie motrice sans local de machine. Download PDF

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Publication number
EP2639194B1
EP2639194B1 EP20120159648 EP12159648A EP2639194B1 EP 2639194 B1 EP2639194 B1 EP 2639194B1 EP 20120159648 EP20120159648 EP 20120159648 EP 12159648 A EP12159648 A EP 12159648A EP 2639194 B1 EP2639194 B1 EP 2639194B1
Authority
EP
European Patent Office
Prior art keywords
traction
wall
counterweight
sheave
car
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.)
Not-in-force
Application number
EP20120159648
Other languages
German (de)
English (en)
Other versions
EP2639194A1 (fr
Inventor
Oleg Paul
Thomas Koch
Michael Krämer
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.)
ThyssenKrupp Aufzugswerke GmbH
Original Assignee
ThyssenKrupp Aufzugswerke 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 ThyssenKrupp Aufzugswerke GmbH filed Critical ThyssenKrupp Aufzugswerke GmbH
Priority to ES12159648.0T priority Critical patent/ES2539165T3/es
Priority to EP20120159648 priority patent/EP2639194B1/fr
Priority to RU2013110012A priority patent/RU2627248C2/ru
Priority to CN201310081061.0A priority patent/CN103303765B/zh
Publication of EP2639194A1 publication Critical patent/EP2639194A1/fr
Application granted granted Critical
Publication of EP2639194B1 publication Critical patent/EP2639194B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/0035—Arrangement of driving gear, e.g. location or support
    • B66B11/0045—Arrangement of driving gear, e.g. location or support in the hoistway
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B17/00—Hoistway equipment
    • B66B17/12—Counterpoises
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/02—Guideways; Guides
    • B66B7/023—Mounting means therefor
    • B66B7/027—Mounting means therefor for mounting auxiliary devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/08—Arrangements of ropes or cables for connection to the cars or cages, e.g. couplings

Definitions

  • the present invention relates to a traction sheave elevator with a car guided on at least two car guide rails in a vertical direction, a counterweight guided on at least two counterweight guide rails in the vertical direction, at least one support means coupling the car and the counterweight together ., And a traction sheave drive with a traction sheave over which the at least one support means is guided, and wherein the traction sheave drive is arranged on a traverse.
  • Such a traction sheave elevator is for example from the document EP 1 577 251 A1 known.
  • Traction sheave elevators represent one of the most commonly used elevator types for vertical elevator systems.
  • at least one suspension element is placed over a motor driven traction sheave.
  • a power transmission from the traction sheave on the at least one support means is effected by frictional engagement.
  • the support means is guided in specially shaped grooves of the traction sheave.
  • At one end of the at least one support means of the car is suspended, at an opposite end of the suspension means the counterweight. Counterweight and car thus always move in opposite directions in an elevator shaft, i. when the car moves up, the counterweight moves down and vice versa.
  • Counterweight and car at half full payload have substantially the same masses, so that they are in equilibrium. Differences may, however, result from payloads loaded into the car or from differently acting masses of the suspension element, depending on the respective position of the car and the counterweight, provided that no compensation cable is provided.
  • traction sheave lifts are designed, for example, without a special engine room.
  • the traction sheave drive is arranged in the shaft head. The traction sheave drive may then be in a position that is higher than a maximum position that can be taken up by the car and the counterweight.
  • the traction sheave drive must be stored in the shaft head.
  • solutions are known in which the traction sheave drive is arranged in a niche in the shaft head or stored on carriers, which in turn are supported in niches of the elevator shaft.
  • all of these solutions are based on the fact that the building or the walls of the elevator shaft must be modified in a certain way in order to install the elevator system can.
  • a support of elements of the elevator installation on a wall of the hoistway over the life of the elevator system is subject to certain relative movements due to a settlement of the building.
  • a guideline can be assumed that a building is set by about one thousandths of its height, the timing of the settlement process is often difficult to predict. For example, in a 100 m high building, it can be assumed that a relative movement between the elevator installation and the shaft wall of about 10 cm will occur.
  • a traction sheave elevator for guiding both the car and the counterweight in a vertical direction, i. a longitudinal direction of the elevator shaft, car guide rails or counterweight guide rails provided.
  • the traverse supported on the at least one counterweight rail must be redesigned for each case of application with respect to the incoming load cases and be calculated. Cheaper here would be independent of the particular application or the dimensioning of the counterweight solution.
  • the publication DE 10 2005 060 838 B3 shows a cable lift with an elevator car, which is movable on a pair of cabin guide rails, with a counterweight which is movable on a pair of counterweight guide rails, and with a shaft provided in the head drive, which has a traction sheave connected to a drive motor on a cross member, wherein the cross member attached to the upper end of the car guide rails.
  • the cross member In order to simply move the cross member with the drive up to the upper end of the car guide rails and fasten there, the cross member at its opposite ends on guide elements, by means of which the cross member with the drive on the car guide rails is ACbewegbar.
  • the publication WO 2010/065038 A1 shows an elevator system in which a portion of a machine storage projects into the elevator shaft.
  • the traverse is fastened to at least one of the car guide rails and further comprises at least one wall attachment for attaching the crossbar to a wall of a hoistway, the at least one wall attachment in each case in a horizontal vertical to the vertical direction and to the wall Direction is positively formed and allowed in the vertical direction, a relative movement between the traverse and the wall, the traction sheave elevator having a plurality of support means, wherein the support means are guided centrally in the counterweight and divided into two suspension strands are deflected around the counterweight and counterweight ends of the support means each attached to the crossbar.
  • the wall attachment By absorbing the horizontal forces, the wall attachment also serves as a support for acting around a longitudinal axis of the traverse moments.
  • the car guide rail is arranged centrally with respect to a longitudinal extension of the cross member on the crossbar.
  • two or four wall mountings can be provided, wherein in each case an equal number of wall mountings are arranged on each side in at least one car guide rail.
  • the wall attachments may then extend perpendicular to a longitudinal extent of the crosshead on the counterweight to the elevator wall.
  • the proposed arrangement may allow the crossbar not to span the entire width of the elevator shaft, i. must extend from a wall to the opposite wall, and thus always be the same or independent of an actual shaft width may be formed.
  • a "suspension element” is understood to be any flexible connection element with which weight forces can be transmitted.
  • the suspension element may be a suspension cable.
  • a suspension cable can be a wire rope, for example. Of steel, or even to a Synthetic rope, for example. From a plastic act.
  • the support means may also be a band, for example a steel band, a chain, a fiber rope, a belt or a belt.
  • the at least one wall fastening each have at least two mutually vertically spaced mounting arrangements in a support spacing, wherein each of the mounting arrangements is positively formed in the horizontal direction and in the vertical direction, a relative movement between the traverse and the wall allowed.
  • the wall mounting can take up moments particularly well. Cheaper leverage results here, the greater the support distance between the mounting arrangements.
  • the support distance is equal to a diameter of the traction sheave.
  • the at least one wall attachment is designed as freewheel in the vertical direction, wherein a movement of the wall is free relative to the traverse down and an opposite movement is at least partially blocked.
  • the freewheel can be designed in the form of two saw tooth profiles which can be displaced relative to one another, wherein one of the profiles is biased in the horizontal direction by means of a spring arrangement.
  • a section-wise locking of the relative movement in the opposite direction can be provided.
  • a roller element can be provided which rolls on a plane and whose rotation is locked in one direction, so that the wall can move relative to the wall mounting only down.
  • the at least one wall attachment is non-positively formed in the vertical direction.
  • Such a non-positive connection can be provided for example by means of a screw connection, wherein the screw is tightened by means of a predetermined torque and / or a spring element.
  • a force must first be provided at a certain height to overcome the static friction and to allow the relative movement between the wall and the wall mounting.
  • the wall attachment in any case is able to absorb forces in the vertical direction at least up to the force necessary to overcome the static friction.
  • the traverse has a first cross member, on which the traction sheave drive is arranged, and a second cross member, which is connected to the at least one wall attachment, wherein the first cross member and the second cross member coupled to each other elastically are.
  • the traction sheave elevator may comprise two car guide rails located in a car guide rail plane, the traction sheave elevator having two counterweight guide rails lying in a counterweight guide rail plane, and the car guide rail plane being perpendicular to the counterweight guide rail plane.
  • the car guide rail plane intersects the counterweight guide rail plane in the middle between the counterweight guides.
  • the car guide rails are all arranged on one side of the counterweight guide rail plane.
  • the counterweight may extend over an entire depth of the hoistway and need only have a small width to provide the desired counterweight mass. In this way, a particularly favorable ratio of the areas of car and counterweight results compared to the surface of the elevator shaft.
  • the traction sheave drive is arranged such that a drive axis of the traction sheave drive is parallel to the counterweight guide rail plane.
  • a longitudinal extension of the traverse then also runs parallel to the counterweight guide rail plane. In this way, a particularly simple and inexpensive cable guide is achieved. Furthermore, the counter moments caused by the traction sheave drive about the drive axle can be supported particularly well by the wall fasteners.
  • the traction sheave drive and the counterweight are arranged such that a center of the counterweight lie in a pulley plane in the car guide rail plane.
  • the support means of the traction sheave can be guided directly down in the middle counterweight. Furthermore, the support means on the opposite side of the traction sheave can be led down directly to the car in order to carry or wrap it around at the top or the underside of the driving cab. In this way, no torque loads are caused perpendicular to the car guide rail plane or pulley plane.
  • the traction sheave elevator has a plurality of support means, wherein a number of the support means is an even number. In principle, of course, an odd number of support means can be provided.
  • the traction sheave elevator 4, 6 or 8 has support means.
  • the traction sheave elevator has a plurality of support means, wherein the support means are guided centrally in the counterweight and divided into two suspension element strands are deflected around the counterweight and counterweight ends of the support means are respectively attached to the cross member.
  • the counterweight ends of the support means are elastically coupled to the crossbar.
  • each of the suspension means thus carries an equally high load.
  • the counterweight is surrounded by the suspension elements symmetrically with respect to the car guide rail.
  • the traction sheave drive projects into a projection surface of the car.
  • a diameter of the traction sheave is 250 mm to 520 mm.
  • the typical diameter of the traction sheave may be 250 mm, 360 mm, 440 mm or 520 mm. In principle, the diameter of the traction sheave should be made as small as possible. In one arrangement, a pulley plane perpendicular to a longitudinal extension of the traverse of the pulley diameter determines the lever acting in the support means forces to initiate moments in the crosshead, a small pulley diameter can minimize these moments.
  • the traction sheave elevator at least two wall mountings, in particular exactly two or exactly four wall mountings, which are arranged symmetrically to the car guide rail plane.
  • the number of wall fasteners may vary depending on the speed and maximum load capacity of the elevator installation.
  • the symmetrical arrangement relative to the car guide rail plane in turn allows the symmetrical absorption of forces and can avoid any further support of the crossbar on a wall of the vehicle shaft.
  • the at least one fastening arrangement has a slot extending in the vertical direction with a guide element, for example a screw, extending through the slot.
  • the traction sheave elevator has a Tragstoffenden peculiar for receiving a respective car-side end of the at least one support means, wherein the Carrier end support is mounted in at least one of the car guide rails and by means of at least one support mounting arrangement on the wall of the elevator shaft, wherein the support mounting arrangement is positively formed in the horizontal direction and in the vertical direction allows a relative movement between the Tragstoffenden peculiar and the wall.
  • a cross-member may also be provided on a car-side end of the suspension element, in which the car-side end of the at least one suspension element is fastened.
  • This truss is then also supported on a car guide rail and a wall of the hoistway.
  • the attachment of the traverse on the wall of the elevator shaft is then carried out in the same manner as that of the traverse on which the traction sheave drive is arranged. In this way it becomes possible to arrange both the counterweight and the car in a 2: 1 suspension.
  • a building setting can cause any tension in both the car side and in the counterweight attachment of the support means.
  • the at least one wall attachment has exactly two mutually spaced mounting arrangements which form a moment support, wherein tensile forces are introduced into the wall by means of one of the fastening arrangements and introduced pressure forces into the wall by means of the other of the fastening arrangements become.
  • the wall mounting can take up moments particularly well.
  • the structural design is easy to install and maintain with little effort.
  • Fig. 1 shows a schematic representation for explaining the terms "positive fit” and "non-positively”, as understood in the present application. Shown are a first element 1 and a second element 2.
  • the first element 1 has a first surface 3.
  • the second element 2 has a second surface 4.
  • the surfaces 3 and 4 are parallel to each other and should be supported on each other. The support of the surfaces 3 and 4 to each other then positive fit when the surfaces 3 and 4 are perpendicular to the direction of a force to be supported 5. This means that an angle 6 between the vector of the force 5 and the course of the surfaces 3 and 4 supported on each other is exactly 90 °.
  • the connection of the surfaces 3 and 4 with respect to the force 5 is form-fitting. No matter how big the force 5, there is no relative movement between the surfaces 3 and 4 instead.
  • a connection between the surfaces 3 and 4 can then be non-positive, if the angle 6 is smaller than 90 °.
  • a relative movement between the surfaces 3 and 4 would then be possible with a sufficiently large force F, if the force F becomes large enough and is transferred from the adhesive into the sliding friction. Accordingly, the connection between the surfaces 3 and 4 would be frictional up to this limit for the transition between static and sliding friction.
  • oblique, ie at an angle 6 of less than 90 ° attacking forces can thus always disassemble by means of a vector decomposition into two forces, one of which like in the Fig. 1 shown force 5 is perpendicular to the surfaces 3 and 4 and one parallel to the surfaces 3 and 4 extends. Perpendicular to the surfaces 3 and 4 then always a positive connection is provided. The greater this force component acting perpendicularly to the surfaces 3 and 4, the greater, however, is the static friction limit. A smaller angle 6 of the attacking force 5 thus always causes the faster transition from static friction to sliding friction.
  • a “positive locking” is understood to mean that the surfaces supported on each other are perpendicular to the direction of the force to be supported.
  • a “frictional connection” is meant a connection in which the abutted surfaces are not vertical, i. at an angle of less than 90 °, in the direction of the force to be supported.
  • Fig. 2 shows an isometric view of a traction sheave elevator 10.
  • the direction X corresponds to a vertical direction.
  • a horizontal plane is spanned by the spatial directions Y and Z.
  • the traction sheave elevator 10 In the traction sheave elevator 10, there is provided a car 12 to be moved in the vertical direction X.
  • the traction sheave elevator 10 has a counterweight 14 which is connected to the car 12 via one or more suspension means (in the Fig. 2 not shown) is coupled.
  • the counterweight 14 may be connected to the car 12, for example, by means of a 1: 1 suspension or 2: 1 suspension known per se to those skilled in the art.
  • the car 12 is guided by means of a first car guide rail 16 and a second car guide rail 18 in its vertical movement.
  • the counterweight 14 is similarly guided by a first counterweight guide rail 20 and a second counterweight guide rail 22 in its vertical movement. The counterweight 14 and the car 12 thus move in opposite directions in the vertical direction X.
  • the traction sheave elevator 10 has a plurality of first holding elements 24, which have the cross-sectional shape of U-shaped brackets.
  • the support members 24 connect the counterweight guide rails 20, 22 and the first car guide rail 16 to a wall (in FIG Fig. 2 not shown).
  • the counterweight 14 thus runs within the U-shaped first holding elements 24.
  • a plurality of second holding members 26 are provided, the second car guide rail 18 on the wall (in the Fig. 2 not shown).
  • a traction sheave 28 is provided.
  • the traction sheave drive 28 on a traction sheave 30 over which the at least one support means of the drive pulley elevator 10 is guided may be mounted centrally in the traction sheave drive 28, but it may also be cantilevered.
  • the car 12 can be moved in the vertical direction X and reciprocated between doors 32 of several floors.
  • Schematically illustrated is an opening mechanism 34 of each door 32, which may cooperate with, for example, a door drive 36 provided on the car 12 to open and close a corresponding door 32.
  • FIG. 2 shown view of the car 12 is equipped with a top plate assembly 38 through which the at least one support means is guided.
  • a bottle arrangement can be provided, which wraps the car 12 on its underside.
  • the traction sheave elevator 10 has a traverse 40 on which the traction sheave drive 28 is arranged.
  • the crossbar 40 has a first cross member 42 and a second cross member 44.
  • the first truss member 42 and the second truss member 44 are elastically coupled together.
  • the traction sheave drive 28 is arranged on the first cross member 42.
  • elastic dampers may be provided between the first traverse element 42 and the second traverse element 44, which may possibly damp vibrations induced by the traction sheave drive 28.
  • the second truss member 44 is centrally supported on the first car guide rail 16. There, an upper end of the car guide rail 16 is connected to the second truss member 44. Furthermore, the traction sheave elevator 10 has a first wall mounting 46 and a second wall mounting 48, the second truss member 44 and one in the Fig. 3 connect wall not shown. The first wall mount 46 and the second wall mount 48 extend over the counterweight 14 and the counterweight guide rails 20 and 22, respectively. The counterweight guide rails 20, 22 thus terminate below the first wall fixture 46 and the second wall fixture 48. In this way, it is possible to design the crossmember 40 independently of the actual dimensions of a manhole and a constant width (Z-camming).
  • the wall mounts 46, 48 can be kept equal regardless of the actual dimensions of the hoistway by keeping a depth (extension Y direction) of the counterweight constant. In this way, there is always an equal distance of the first car guide rail 16 from the wall. A corresponding mass of the counterweight 14 may then be provided by optimally utilizing the width (extension Z direction) of the duct below a corresponding length (extension X direction) of the counterweight 14.
  • the wall mounts 46, 48 are configured to receive the forces in the Y direction but allow relative movement between the respective wall mounts 46, 48 and the wall of the chute in the X direction , In this way, a building set can be compensated at this point.
  • a building-independent storage of the traction sheave drive 28 of the traction sheave elevator 10 can be provided, which allows a compact structure and at the same time avoids problems caused by a building setting problems.
  • the traction sheave elevator 10 has a carrier means carrier 49.
  • the support means end support 49 is connected to the wall and the second car guide rail 18 in the same manner as the first wall attachment 46 and the second wall attachment 48 such that forces in the X direction are introduced directly into the second car guide rail 18 and forces in the Y direction and in the Y direction Moments can be supported on the wall.
  • a relative movement of the attachment of the Tragstoffendenlys 49 on the wall in the X direction relative to the wall is possible.
  • the Fig. 4 shows a schematic plan view of the traction sheave elevator 10, from which the geometric arrangement of the individual elements of the traction sheave elevator 10 is relative to each other.
  • the illustrated traction sheave elevator 10 is shown with the possibility of a through-loading. That there are two opposing doors 32 are provided on each floor. Of course, this is only to be understood as an example. In principle, only one door 32 can be provided.
  • a shaft in which the traction sheave 10 is arranged is designated by a reference numeral 50.
  • the shaft is bounded by a wall 52.
  • the course of the at least one support means shown schematically.
  • the course is illustrated by the example of two suspension elements.
  • a reference numeral 54 the location is marked, at which the support means are guided by the traction sheave 30 down in the direction of the car 12.
  • the support means are then guided, for example, through the upper bottle 38 and run back up, where their car-side end 58 is fixed to the Tragstoffendengina 49.
  • the support means are guided at a location 56 down into the counterweight 14. They wrap around the counterweight 14 and are then guided back up and fixed with their counterweight-side ends 60 to the crossbar 40 and in the second cross member 44.
  • a counterweight guide rail level 62 is shown. This runs through the first counterweight guide rail 20 and the second counterweight guide rail 22.
  • a drive shaft 63 of the traction sheave drive 28 extends parallel to the counterweight guide rail plane 62 and denotes the axis about which the traction sheave 30 rotates.
  • a car guide rail 64 Perpendicular to both the counterguide rail 62 and the drive axle 63 is a car guide rail 64 which extends between the first car guide rail 16 and the second car guide rail 18.
  • the car guide rails 16 and 18 guide the car 12 in the middle.
  • the traction sheave 30 rotates about the drive shaft 63. Perpendicular to the drive shaft 63 extends through the center of the traction sheave 30 a pulley plane 66.
  • the pulley plane 66 extends in the car guide rail plane 64th
  • the symmetrically designed in this way arrangement of the entire traction sheave elevator 10 substantially reduces the introduced into the Traverse 40 moments.
  • a diameter D of the traction sheave 30 is also chosen to be as small as possible in order to keep a distance of the down-driven ropes 54, 56 to the drive axle 63 as low as possible. In this way, moment loads in the crosshead 40 about the Z axis are kept low.
  • the symmetrical arrangement of the traction sheave elevator 10 also provides symmetrical loading of the traverse about the Y axis. The load cases occurring in this way can be integrated directly into the first car guide rail 16 and the two wall mountings 46, 48, which are arranged symmetrically to the car guide rail plane 64, are received. In particular, it may be provided that the drive axle 63 and the car guide rail plane 64 intersect over the first car guide rail 16.
  • the traction sheave drive 28 or the traction sheave 30 projects into a projected area 70 of the car 12.
  • the projected area 70 is thus in the in Fig. 4 illustrated cross-sectional view visible cross-sectional area of the car 12, which is projected onto the height of the traction sheave drive 28.
  • Fig. 5 shows in a plan view schematically a guide of a first support means 72 and a second support means 74 to the counterweight 14.
  • the same elements are in the Fig. 5 denoted by the same reference numerals and will not be explained again.
  • the support means 72, 74 are guided by the traction sheave 30 down through the counterweight 14 and share after passing through the counterweight 14 in a first suspension element strand 76 and a second suspension element strand 78.
  • first suspension element strand 76 and a second suspension element strand 78 In the illustrated embodiment with only two support means 72, 74 has correspondingly each support means strand 76, 78 on a support means.
  • embodiments with four, six or eight support means are also conceivable, so that then each suspension element strand 76, 78 has two, three or four suspension elements.
  • Corresponding deflection rollers 80 may be provided on an underside or also on an upper side of the counterweight 14 in order to guide the suspension element strands 76, 78 away from the car guide rail plane 64 to the outside.
  • the suspension element strands 76, 78 are thus deflected symmetrically outwards from the car guide rail plane 64 and pass through the latter at opposite ends of the counterweight 14.
  • the counterweight-side ends 60 of the suspension element strands 76, 78 are then on the second truss element 44 of Traverse 40 attached. In this way, a load of the crosshead 40 symmetrical with respect to the car guide rail plane 64 is provided. A moment loading around the Y-axis of the crossbar 40 by the counterweight suspension can be kept so small and symmetrical.
  • Fig. 6 shows a top view of the crossbar 40.
  • the same elements are again identified by the same reference numerals and will not be explained again.
  • the traction sheave drive 28 is shown, which is arranged on the second cross member 44.
  • the second truss element is coupled to the second truss element 44 by means of a first damper 82 and a second damper 83. In this way, for example, a vibration damping between the first and the second truss member 42, 44 can be achieved.
  • the second truss member 44 has the first and second wall mount 46, 48 and is connected thereto by a plurality of wall anchors 86 to the wall 52.
  • the attachment of the first wall attachment 46 with the second wall attachment 48 in the wall 52 can be done, for example, with the aid of dowels.
  • first suspension element strand 76 on the second cross member 44 is partially cut free.
  • a third elastic element 84 which elastically couples the first suspension element strand 76 with the second cross member 44.
  • the entire first suspension element strand 76 is elastically coupled to the second transverse element 44.
  • each cable of the first suspension element strand is elastically coupled to the second transverse element 44 in order to provide a uniform load distribution on all suspension elements.
  • Fig. 7 is a side view of the crossbar 40 from Fig. 6 shown.
  • each fastening arrangement 88, 90 is designed such that it is configured in a form-locking manner in a horizontal direction (Y) and is frictionally configured in a vertical direction (X).
  • each fastening arrangement 88, 90 has a slot 92 or 94 through which a guide element, for example a screw 96 or 98, is guided. The screw thus connects a wall element 102 connected to the wall by means of the wall anchor 86 and a support element 104 connected to the second cross member 44.
  • a force can be set which is sufficient to overcome a frictional connection between a respective guide element or a respective screw 96, 98 and the wall element 102. Then, a relative movement between the wall 52 connected to the wall member 102 and the support member 104 connected to the second cross member 44 is possible, so that a building setting can be done without forces or stresses in the cross member 40 occur.
  • the shank of a respective guide element or a respective screw 96, 98 is perpendicular to the edge of the respective slot 92, 94, so that a positive connection is provided.
  • Forces in the Y direction can thus be accommodated by both the first attachment assembly 88 and the second attachment assembly 90.
  • the first wall mount 46 can thus serve as a torque arm for moments about the Z axis, which are introduced from the crossbar 40 in the first wall mount 46.
  • a support distance 100 between the first fastening arrangement 88 and the second fastening arrangement 90 or between the guide elements or screws 96, 98 should be as large as possible. In order not to let the overall dimensions of the first wall attachment 46 become too large, it has been found that for good leverage ratios the support distance 100 should correspond approximately to the diameter D of the traction sheave 30.
  • a respective fastening arrangement 88, 90 it is not mandatory for a respective fastening arrangement 88, 90 to provide a force fit in the X direction or the vertical direction. In this direction, a freewheel can be provided.
  • a first freewheeling element and a second freewheeling element are arranged relative to one another in such a way that they provide positive locking in the Y direction but have two sawtooth profiles in the Z direction which shift relative to one another in the X direction or vertical direction can.
  • the first freewheeling element 106 is tensioned toward the second freewheeling element 108 by means of a spring element 109.
  • the first freewheeling element 106 which is fixedly connected to the wall 52, could move downwards (U) to the second freewheeling element 104, which is connected to the second crossbar element 44.
  • a cable retention assembly 110 for attaching a far end 58 of the support means 72, 74 is shown.
  • Each support means 72, 74 is held in an opening 111 of the Tragstoffendenlys 49.
  • the support means end support 49 is further connected to the second car guide rail 18 (in FIGS Fig. 9 not shown) so that forces acting in the X direction can be introduced directly into the second color basket guide rail 18.

Claims (14)

  1. Ascenseur à poulie motrice (10) comprenant une cabine (12) qui est guidée dans une direction verticale au moins sur deux rails de guidage de cabine, un contrepoids (14) qui est guidé dans la direction verticale (X) au moins sur deux rails de guidage de contrepoids (20, 22), au moins un moyen porteur (72, 74) qui accouple l'un à l'autre la cabine (12) et le contrepoids (14), et un entraînement à poulie motrice (28) comprenant une poulie motrice (30) par le biais de laquelle l'au moins un moyen porteur (72, 74) est guidé, et l'entraînement à poulie motrice (28) étant disposé sur une traverse (40), la traverse (40) étant fixée à au moins l'un des deux rails de guidage de cabine (16, 18) et comprenant en outre au moins une fixation de paroi (46, 48) pour fixer la traverse (40) à une paroi (52) d'une cage d'ascenseur (50), l'au moins une fixation de paroi (46, 48) étant réalisée de manière à présenter respectivement une complémentarité de formes dans une direction horizontale (Y) perpendiculaire à la direction verticale (X) et à la paroi et permettant un déplacement relatif entre la traverse (40) et la paroi (52) dans la direction verticale (X), caractérisé en ce que l'ascenseur à poulie motrice (10) comprend plusieurs moyens porteurs (72, 74), les moyens porteurs (72, 74) étant guidés centralement dans le contrepoids (14) et étant déviés autour du contrepoids (14) de manière devisée en deux brins de moyen porteur (76, 78), et des extrémités (60) du côté du contrepoids des moyens porteurs (72, 74) étant fixées respectivement à la traverse (40).
  2. Ascenseur à poulie motrice selon la revendication 1, caractérisé en ce que l'au moins une fixation de paroi (46, 48) comprend respectivement au moins deux ensembles de fixation (88, 90) espacés verticalement l'un de l'autre à une distance de support (100), chacun des ensembles de fixation (88, 90) étant réalisé de manière à présenter une complémentarité de formes dans la direction horizontale (Y) et permettant un déplacement relatif entre la traverse (40) et la pa.roi (52) dans la direction verticale (X).
  3. Ascenseur à poulie motrice selon la revendication 1 ou 2, caractérisé en ce que l'au moins une fixation de paroi (46, 48) est réalisée sous forme de roue libre (106, 108) dans la direction verticale (X), un déplacement de la paroi (52) par rapport à la traverse (40) vers le bas (U) étant libre et un déplacement opposé étant au moins en partie bloqué.
  4. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'au moins une fixation de paroi (46, 48) est réalisée de manière à présenter un engagement par force dans la direction verticale (X).
  5. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la traverse (40) comprend un premier élément de traverse (42) sur lequel l'entraînement à poulie motrice (28) est disposé, et un deuxième élément de traverse (44) qui est relié à l'au moins une fixation de paroi (46, 48), le premier élément de traverse (42) et le deuxième élément de traverse (44) étant accouplés élastiquement l'un à l'autre.
  6. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'ascenseur à poulie motrice (10) comprend deux rails de guidage de cabine (16, 18) qui sont situés dans un plan de rails de guidage de cabine (64), l'ascenseur à poulie motrice comprenant deux rails de guidage de contrepoids (20, 22) qui se situent dans un plan de rails de guidage de contrepoids (62), et le plan de rails de guidage de cabine (64) étant disposé perpendiculairement au plan de rails de guidage de contrepoids (62).
  7. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'entraînement à poulie motrice (28) est disposé de telle sorte qu'un axe d'entraînement (63) de l'entraînement à poulie motrice (28) s'étende parallèlement au plan de rails de guidage de contrepoids (62).
  8. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 7, caractérisé en ce que l'entraînement à poulie motrice (28) et le contrepoids (14) sont disposés de telle sorte qu'un centre (68) du contrepoids (14) et un plan de poulie motrice (66) se situent dans le plan de rails de guidage de cabine (64).
  9. Ascenseur à poulie motrice selon la revendication 1, caractérisé en ce que les extrémités (60) du côté du contrepoids des moyens porteurs (72, 74) sont accouplées élastiquement à la traverse (40).
  10. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 9, caractérisé en ce que l'entraînement à poulie motrice (28) fait saillie dans une surface de projection (70) de la cabine (12).
  11. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 10, caractérisé en ce que l'ascenseur à poulie motrice (10) comprend au moins deux fixations de paroi (46, 48) qui sont disposées symétriquement par rapport au plan de rails de guidage de cabine (64).
  12. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 11, caractérisé en ce que l'au moins un ensemble de fixation (88, 90) comprend un trou oblong (92, 94) s'étendant dans la direction verticale (X) avec un élément de guidage (96, 98) s'étendant à travers le trou oblong (92, 94).
  13. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 12, caractérisé en ce que l'ascenseur à poulie motrice (10) comprend un support d'extrémité de moyen porteur (49) pour recevoir une extrémité (58) respective du côté de la sabine de l'au moins un moyen porteur (72, 74), le support d'extrémité de moyen porteur (49) étant fixé à au moins l'un des rails de guidage de cabine (16, 18) et à la paroi (52) de la cage d'ascenseur (50) au moyen d'au moins un ensemble de fixation de support (110), l'ensemble de fixation de support (110) étant réalisé de manière à présenter une complémentarité de formes dans la direction horizontale (Y) et permettant un déplacement relatif entre le support d'extrémité de moyen porteur et la paroi (52) dans la direction verticale (X).
  14. Ascenseur à poulie motrice selon l'une quelconque des revendications 1 à 13, caractérisé en ce que l'au moins une fixation de paroi (46, 48) comprend respectivement exactement deux ensembles de fixation (88, 90) espacés l'un de l'autre, lesquels forment un support de couple, des forces de traction étant appliquées dans la paroi (52) au moyen de l'un des ensembles de fixation (88) et des forces de compression étant appliquées dans la paroi (52) au moyen de l'autre des ensembles de fixation (90) .
EP20120159648 2012-03-15 2012-03-15 Ascenseur à poulie motrice sans local de machine. Not-in-force EP2639194B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES12159648.0T ES2539165T3 (es) 2012-03-15 2012-03-15 Ascensor de polea motriz sin sala de máquinas
EP20120159648 EP2639194B1 (fr) 2012-03-15 2012-03-15 Ascenseur à poulie motrice sans local de machine.
RU2013110012A RU2627248C2 (ru) 2012-03-15 2013-03-05 Лифт с канатоведущим шкивом без помещения для приводного механизма
CN201310081061.0A CN103303765B (zh) 2012-03-15 2013-03-14 不带有机房的摩擦轮式电梯

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20120159648 EP2639194B1 (fr) 2012-03-15 2012-03-15 Ascenseur à poulie motrice sans local de machine.

Publications (2)

Publication Number Publication Date
EP2639194A1 EP2639194A1 (fr) 2013-09-18
EP2639194B1 true EP2639194B1 (fr) 2015-03-11

Family

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Application Number Title Priority Date Filing Date
EP20120159648 Not-in-force EP2639194B1 (fr) 2012-03-15 2012-03-15 Ascenseur à poulie motrice sans local de machine.

Country Status (4)

Country Link
EP (1) EP2639194B1 (fr)
CN (1) CN103303765B (fr)
ES (1) ES2539165T3 (fr)
RU (1) RU2627248C2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016002042A1 (fr) * 2014-07-03 2016-01-07 三菱電機株式会社 Ascenseur sans salle des machines
WO2016166563A1 (fr) 2015-04-17 2016-10-20 Otis Elevator Company Système d'ascenseur
CN107601221A (zh) * 2017-08-18 2018-01-19 江苏天奥电梯有限公司 一种曳引式钢带传动电梯
CN108946398A (zh) * 2018-08-08 2018-12-07 佛山菱王科技有限公司 钢带电梯

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI100516B (fi) * 1994-09-27 1997-12-31 Kone Oy Järjestelyt hissiköyden kiinnittämiseksi ja johteen käyttämiseksi hiss in kannatuselimenä
EP1215157B1 (fr) 1998-07-13 2005-03-30 Inventio Ag Disposition de la machinerie d'ascenseur
AU2002228028B2 (en) * 2001-01-04 2006-04-13 Kone Corporation Gearless cable lift with a dual wind drive disk mechanism
DE50209383D1 (de) * 2001-11-23 2007-03-15 Inventio Ag Aufzug mit riemenartigem übertragungsmittel, insbesondere mit zahnriemen, als tragmittel und/oder treibmittel
JP4229633B2 (ja) * 2002-04-26 2009-02-25 東芝エレベータ株式会社 マシンルームレスエレベータ
DE20207439U1 (de) * 2002-05-11 2002-10-31 Tepper Aufzuege Gmbh & Co Kg Antriebswippe
IL157277A (en) 2002-09-05 2007-12-03 Inventio Ag Elevator and method of arranging the motor of an elevator
IL180964A (en) * 2002-09-05 2010-11-30 Inventio Ag Drive engine for a lift installation and method of mounting a drive engine
JP2004142927A (ja) * 2002-10-28 2004-05-20 Toshiba Elevator Co Ltd エレベータ装置
JP2005154116A (ja) * 2003-11-27 2005-06-16 Toshiba Elevator Co Ltd エレベータロープの端末支持装置
PT1698581E (pt) * 2005-03-01 2011-10-19 Ind Montanesas Electricas Mecanicas S L Máquina, sistema elevatório e elevador sem casa das máquinas
DE102005060838B3 (de) * 2005-12-20 2007-03-01 Aufzugswerke M. Schmitt & Sohn Gmbh & Co. Seilaufzug
KR101226976B1 (ko) * 2008-12-05 2013-01-28 오티스 엘리베이터 컴파니 엘리베이터 기계 지지체

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Publication number Publication date
RU2627248C2 (ru) 2017-08-04
RU2013110012A (ru) 2014-09-10
ES2539165T3 (es) 2015-06-26
CN103303765B (zh) 2017-09-05
EP2639194A1 (fr) 2013-09-18
CN103303765A (zh) 2013-09-18

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