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
  • B66B11/0055—Arrangement of driving gear, e.g. location or support in the hoistway on the counterweight
• • 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
  • B66B11/0065—Roping
  • B66B11/008—Roping with hoisting rope or cable operated by frictional engagement with a winding drum or sheave

Definitions

• the present invention relates to elevator systems and, more particularly, to an elevator system requiring less installation and operation space than conventional elevator systems by utilizing combined function structures including a counterweight-drive assembly and a belt that shares drive belt and suspension rope functions.
• the hoistway is an elongated, vertical shaft having a rectangular base in which the elevator car translates.
• the hoistway houses, among other things, the car guide rails which are usually a pair of generally parallel rails, fixed to opposite walls near the center of each wall, and running the approximate length of the hoistway.
• a counterweight having a pair of guide rails is positioned adjacent to a third wall.
• the hoistway houses additional components including terminal landing switches, ropes and sheave arrangements, and buffers for the counterweight and the car.
• the elevator components are located and oriented with precision prior to and during operation.
• the interior walls of the hoistway must be properly dimensioned and aligned, and the physical interface between the hoistway walls and the elevator components must be capable of withstanding varying load during use.
• the guide rails on which the car rides are properly positioned and solidly maintained.
• Guide rails are typically steel, T-shaped sections in sixteen foot lengths.
• the position of guide rails within the hoistway affects the position of the hoisting machine, governor and overhead (machine room) equipment.
• the machine room is typically located directly above the hoistway.
• the machine room houses the hoist machine and governor, the car controller, a positioning device, a motor generator set, and a service disconnect switch.
• the present invention achieves the aforementioned and other objects by utilizing an assembly of a drive machine and components housed within and moveable with a counterweight, as well as a shared rope or belt which functions both as a drive belt and as a suspension rope.
• the counterweight- drive assembly includes a motor and drive pulley sized to maintain a narrow profile and to be suspended and to move in coordination with an elevator car.
• the use of flat ropes or belts reduces the size of the traction sheave and motor required such that the machine can have a narrow profile, enabling a machine- counterweight assembly to fit between the elevator car and the hoistway wall.
• flat ropes refers to ropes or belts having an aspect ratio of greater than one, where aspect ratio is defined as the ratio of the rope or belt width to the thickness.
• the counterweight-drive assembly is coupled to an elevator car by being suspended from the same belt or rope which is fixed relative to the hoistway at both ends. When torque is applied through the drive pulley, the counterweight-drive assembly is caused to climb the belt and move up or down the hoistway. It is preferable to use a flat belt or rope for optimum traction and low weight.
• Fig. 1 is a schematic view of the present invention elevator assembly showing the elevator car and the counterweight drive assembly at a common height.
• Fig. 2 is a schematic view of the elevator assembly as shown in Fig. 1 showing the elevator car in a lowered position and the counterweight-drive assembly in a raised position.
• Fig. 3 is a schematic view of a component of the elevator assembly of Fig. 1 showing the elevator car in a raised position and the counterweight- drive assembly in a lowered position.
• Fig. 4 is a sectional, side view of a traction sheave and a plurality of flat ropes, each having a plurality of cords.
• Fig. 5 is a sectional view of one of the flat ropes. Description of the Preferred Embodiments
• An elevator assembly according to the present invention is illustrated schematically in Figs. 1-3.
• An elevator assembly (10) includes an elevator car (12) and a counterweight-drive assembly (14), each being suspended from a belt (16) which is fixed at first (18) and second (20) ends to a hoistway ceiling surface (22) or other fixed structure.
• the counterweight-drive assembly (14) comprises a body (24) housing a drive assembly (not shown) including a motor. Components of the drive assembly include a drive pulley (26) adapted to provide torque from the motor, and a brake mechanism (28).
• the motor (not shown) can be an electric motor and can be supplied power and control signals via a power and control cable (30) in communication with a power and control source (32).
• the cable (30) is adapted to move with the counterweight-drive assembly (24).
• the motor (not shown), is preferably of the flat machine type having, for example, a disc-type rotor with the rotational axis of the machine perpendicular to the width of the counterweight.
• the use of flat ropes with this type of machine minimizes torque requirements of the motor and therefore minimizes the diameter of the disc-type rotor. This enables the counterweight and machine to fit between the car (12) and the hoistway wall.
• a cylindrical machine may be used in which the rotational axis is parallel to the width of the counterweight.
• a first idler pulley (34) is fixed to the hoistway ceiling (22) or other stationary surface and pivotally engages the belt (16).
• a second idler pulley (36) is fixed to the elevator car (12) and also pivotally engages the belt (16).
• the length of belt (16) between the drive pulley (26) and the first end (18) is shortened, and the remaining length between the drive pulley (26) and the first idler pulley (34) will shorten to maintain tension in the belt between the first idler pulley (34) and the first end (18).
• the length of belt ( 16) between the first idler pulley (34) and the second end (20) of the belt (16) will increase as gravity acts on the elevator car (12).
• the counterweight-drive assembly (24) will stop moving and the elevator car (12) will settle in an equilibrium position as shown.
• the counterweight- drive assembly (24) is caused to move away from the first end (18) of the belt (16).
• the length of belt (16) between the drive pulley (26) and the first end (18) is increased and, due to gravity, the counterweight-drive assembly (24) will lower.
• the length between the drive pulley (26) and the first idler pulley (34) will also increase as the belt (16) passes freely over the first idler pulley (34).
• the length of belt (16) between the first idler pulley (34) and the second end (20) of the belt (16) will decrease and cause the elevator car (12) to be raised.
• the counterweight-drive assembly (24) will stop moving and the elevator car (12) will settle in an equilibrium position as shown.
• the belt (16) being a flat one for high traction
• the belt may be of a variety of different suitable types including a toothed belt.
• the configuration of the drive mechanism contained in the counterweight-drive assembly (24) may vary in such ways as using a plurality of motors or drive pulleys or sheaves. Other modifications of similar type can be implemented in the present invention without departing from the scope of what is presently claimed.
• a principal feature of the present invention is the flatness of the ropes used in the above described elevator system.
• the increase in aspect ratio results in a rope that has an engagement surface, defined by the width dimension "w", that is optimized to distribute the rope pressure. Therefore, the maximum rope pressure is minimized within the rope.
• the thickness "tl"of the flat rope may be reduced while maintaining a constant cross-sectional area of the portions of the rope supporting the tension load in the rope.
• the flat ropes 722 include a plurality of individual load carrying cords 726 encased within a common layer of coating 728.
• the coating layer 728 separates the individual cords 726 and defines an engagement surface 730 for engaging the traction sheave 724.
• the load carrying cords 726 may be formed from a high-strength, lightweight non- metallic material, such as aramid fibers, or may be formed from a metallic material, such as thin, high-carbon steel fibers. It is desirable to maintain the thickness "d" of the cords 726 as small as possible in order to maximize the flexibility and minimize the stress in the cords 726.
• the fiber diameters should be less than .25 millimeters in diameter and preferably in the range of about .10 millimeters to .20 millimeters in diameter.
• Steel fibers having such diameter improve the flexibility of the cords and the rope.
• the traction sheave diameter "D" may be reduced while maintaining the maximum rope pressure within acceptable limits.
• the engagement surface 730 is in contact with a corresponding surface 750 of the traction sheave 724.
• the coating layer 728 is formed from a polyurethane material, preferably a thermoplastic urethane, that is extruded onto and through the plurality of cords 726 in such a manner that each of the individual cords 726 is restrained against longitudinal movement relative to the other cords 726.
• a polyurethane material preferably a thermoplastic urethane
• Other materials may also be used for the coating layer if they are sufficient to meet the required functions of the coating layer: traction, wear, transmission of traction loads to the cords and resistance to environmental factors. It should be understood that although other materials may be used for the coating layer, if they do not meet or exceed the mechanical properties of a thermoplastic urethane, then the benefits resulting from the use of flat ropes may be reduced.
• the traction sheave 724 diameter is reducible to 100 millimeters or less.
• the rope pressure may be distributed more uniformly throughout the rope 722.
• Cord pressure is decreased at least as n "'/j , with n being the number of parallel cords in the flat rope, for a given load and wire cross section. Therefore, the maximum rope pressure in the flat rope is significantly reduced as compared to a conventionally roped elevator having a similar load carrying capacity.
• the effective rope diameter 'd' (measured in the bending direction) is reduced for the equivalent load bearing capacity and smaller values for the sheave diameter 'D' may be attained without a reduction in the D/d ratio.
• minimizing the diameter D of the sheave permits the use of less costly, more compact, high speed motors as the drive machine.
• a traction sheave 724 having a traction surface 750 configured to receive the flat rope 722 is also shown in Figure 4.
• the engagement surface 750 is complementarily shaped to provide traction and to guide the engagement between the flat ropes 722 and the sheave 724.
• the traction sheave 724 includes a pair of rims 744 disposed on opposite sides of the sheave 724 and one or more dividers 745 disposed between adjacent flat ropes.
• the traction sheave 724 also includes liners 742 received within the spaces between the rims 744 and dividers 745.
• the liners 742 define the engagement surface 750 such that there are lateral gaps 754 between the sides of the flat ropes 722 and the liners 742.
• a traction sheave without liners may be used.
• the present invention eliminates the need for a machine room, requires less total material, and enables use of small diameter drive pulley and idler pulleys with a high-traction flat rope or belt.
• the machine or drive assembly (24) can be accessed either from the bottom of the hoistway or through a window or opening in the elevator car (12) when positioned in alignment.
• the design of the present invention eliminates body-conducted vibrations and noise from the motor to the car (12) or building.
• the flat belt (16) inherently dampens vibrations.
• the counterweight-drive assembly (24) may be pre-assembled and pre-tested to save on installation time and to increase reliability.

Landscapes

• Engineering & Computer Science (AREA)
• Civil Engineering (AREA)
• Mechanical Engineering (AREA)
• Structural Engineering (AREA)
• Lift-Guide Devices, And Elevator Ropes And Cables (AREA)

Applications Claiming Priority (7)

Publications (1)

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• 1999
  • 1999-02-19 EP EP99936069A patent/EP1097102A1/de not_active Withdrawn
  • 1999-02-19 WO PCT/US1999/003647 patent/WO1999043602A1/en active Application Filing

Non-Patent Citations (1)

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