EP1347931A1

EP1347931A1 - Gearless cable lift with a dual wind drive disk mechanism

Info

Publication number: EP1347931A1
Application number: EP01989626A
Authority: EP
Inventors: Horst Wittur; Dietmar KÜNTSCHER; Klaus Fichtner
Original assignee: Wittur AG
Current assignee: Kone Corp
Priority date: 2001-01-04
Filing date: 2001-12-31
Publication date: 2003-10-01
Anticipated expiration: 2021-12-31
Also published as: RU2278812C2; CN1285499C; CN1484608A; ATE305896T1; WO2002053486A1; UA76442C2; EP1347931B1; DE50107638D1; JP2004520245A; RU2003123506A; ES2209675T1; ES2209675T3; US20040129501A1; BR0116709B1; KR20030064890A; KR100725693B1; CZ20031764A3; AU2002228028B2; CZ299209B6; DE10164548A1

Abstract

The invention relates to a gearless cable lift with a drive disk mechanism which is dually wound by several bearer cables, comprising a counter disk (3), an elevator car (6), guide tracks for the elevator car (6) and a counter weight, especially for installation without a machine room. According to the invention, the bearer cables are guided in semicircular grooves and the ratio of the drive disk diameter to the nominal diameter of the bearing cables is < 40.

Description

GEARLESS ROPEWIND WITH DOUBLE WINDING DRIVE DISC DRIVE

The invention relates to a gearless cable elevator with a traction sheave drive double-wrapped by a plurality of parallel support cables with a counter pulley, a car, guide rails for the car and a counterweight, in particular for a machine room-less installation of the elevator machine.

In the case of rope lifts, the car and the counterweight are connected to each other via the rope suspension element. The counterweight balances the dead weight of the car and a part, usually half, of the payload and half the dead weight of the hanging cables leading to the car. For safety reasons, at least two suspension ropes running in parallel are required. Nowadays, cable lifts are equipped with traction sheave drives instead of the cable drum drives that were customary in the past, and the traction sheave can also be designed as a driving ring. Electric motors are used as the drive unit. Traction sheave and drive motor including its energetic and control part are essential components of a gearless elevator machine. Gearless elevator machines are extremely quiet, small and inexpensive. They are more advantageous than geared elevator machines. They do not require an environmentally hazardous gear oil and the loss of the gear improves the efficiency. The elevator machine is installed in a separate machine room or directly in the vehicle shaft. In the latter case, it can be installed in the upper or lower part of the shaft, laterally in the counterweight space or directly on or under the car. Depending on the type of installation, the car payload and other conditions, such as head or speed, different suspension cable guides have developed.

In the simplest case, the simple suspension, the suspension cable coming from the car is guided to the counterweight via the traction sheave permanently installed in the shaft head or in the machine room above it. However, there are also other suspension cables in multiple suspensions, which at the same time implement a specific transmission ratio of rope to car speed using loose rollers. If, for example, the rope drive is designed with a loose roller on the car and a loose roller on the counterweight, the torque of the drive motor is reduced to half at twice the speed. The machine becomes smaller and can be installed more easily in the elevator shaft.

To increase or achieve the required driving ability, it is known to choose a "double wrap", which is then carried out in connection with less noisy and more wear-resistant semicircular grooves.

An arrangement with double wrap through two or more parallel support cables is described for example in DE 36 34 859 AI. The support ropes extending from the car to the counterweight are looped twice around the traction sheave and between these loops once around a deflection sheave, the contact angle between the traction sheave and the support ropes in both loops exceeding the traction sheave. A variant with a double loop and two deflection disks is shown in Fig. 2c of EP 0 578 237 AI.

A machine room-less arrangement with double wrapping around the traction sheave is shown in WO 99/43595. According to Fig. 2, the suspension means, coming from an upper rope stop, double around the traction sheave and counter pulley, both at the bottom of the Car are attached, further up again, where it deflects on a fixed roller and ultimately via a loose roller on the counterweight to a second upper rope stop. The traction sheave and counter pulley are at such a distance from one another that a deflection roller on the car floor is unnecessary. Two parallel flat strands are provided as suspension means, as specified in WO 99/43885, for example. Further flat strands are shown, for example, in WO 98/29327. In contrast to the usual round ropes, flat strands consist of several small, parallel, metallic or non-metallic strands or ropes, which are enclosed together by a flat ribbon-like, non-metallic sheathing. The strand thickness according to WO 99/43885 enables flat strands of extremely small thickness. According to a common calculation rule, according to which the traction sheave diameter should correspond to at least 40 times the carrying rope diameter, traction sheave diameters of 100 mm and below result. Small traction sheave diameters have a direct proportional effect on the torque to be applied and thus on the size of the drive motors. That is, the smaller the traction sheave diameter, the less torque has to be applied to the traction sheave and the more compact and inexpensive the drive motor can be designed.

According to the preceding statements, small traction sheave diameters are particularly advantageous in elevator construction, since they enable the drive motor to be compact. Small traction sheaves, however, have the disadvantage that the suspension rope is used more and the rope life is reduced. In order to ensure a sufficient rope service life in the elevators according to the prior art, traction sheave diameters of at least 40 times the cable diameter are used, the reduction of the cable diameter being achieved by using the flat strands described above as cable cables with a particularly small diameter.

A disadvantage of the flat strands, however, is the need to manufacture and keep special, very costly suspension elements for all load sizes. In addition, incipient damage to the suspension element, which can lead to a serious risk to elevator operation or even safety, can only be detected with considerable technological effort or not at all. The invention has for its object to further develop a gearless cable elevator with double wrap so that the disadvantages of the flat strands are avoided and the elevator has a compact and inexpensive construction.

The object is achieved by the features specified in claim 1. Advantageous further developments are specified in the dependent claims 2 to 21.

Instead of two or three extremely thin flat strands, suspension ropes of the same thickness are always used in the elevator according to the invention, the ratio of the traction sheave diameter to the nominal diameter of the suspension ropes being <40. A ratio of essentially 30 has proven to be very advantageous. This enables small traction sheave diameters, which ensures a compact and inexpensive construction of the drive motor. The reduced rope service life, which results from a reduced traction sheave diameter, is avoided according to the invention through the use of semicircular traction grooves in which the support ropes run. Although the driving ability of the drive pulley is reduced by the use of semicircular grooves, this is compensated for by the use of a double wrap. The suspension cables run in undercut-free driving grooves, but driving grooves with a small undercut, preferably of 1-3 mm, can also be used. Such a small undercut can have a positive effect on the running properties.

The drive torque can be greatly reduced in the cable pull according to the invention, which also makes the drive machine smaller. On the other hand, the suspension cables do not experience such an extreme bending radius and rolling speeds as the flat strands on traction sheaves with a diameter of <100 mm.

The thin suspension cables lie very well in the semicircular grooves of the traction sheave, which are precisely adapted to the suspension cable diameter, which prevents deformation of the cable and transverse pressures and reduces the surface pressure. The suspension ropes therefore have a long lay-on time. Due to the circular cross-section of the suspension ropes, the ropes are "always" found in the half-round len of the driving wheel. As a result, they have no tendency to move out of bed due to vibrations or uneven loads. In addition, noise reduction should not be underestimated.

The invention is therefore based on the knowledge that the combination of a double wrap of the drive cable with the guide in semicircular drive grooves can reduce the ratio of the drive pulley diameter to the nominal diameter of the support cables, as a result of which smaller support cable diameters and thus a more cost-effective construction of the cable elevator with an undiminished long cable service life are ensured becomes.

As a further advantage, it is not necessary to keep different rope strengths or flat strand widths in stock. You can use traction sheaves of a groove size, whereby a traction sheave can be designed over a large or the entire payload range.

The visual inspection of the suspension ropes for fatigue damage, the manual detection of wire breaks with sensing tools and the heat dissipation from the suspension ropes is considerably safer and easier compared to flat plastic strands. The breakage of a strand, strands, crushing, excessive wear or corrosion of the individual wires cannot be detected visually in plastic-coated flat strands and can only be partially determined using magnetic induction methods. The manufacturing and procurement costs of round ropes are considerably lower compared to flat strands. There is no risk of damage from marten bites, which cannot be excluded with flat plastic strands. If the individual strands or individual ropes of a plastic-coated flat strand are of different lengths, the entire flat strand warps and its driving capacity and lay-up time are reduced.

In a particularly preferred embodiment of the invention, particularly thin suspension cables with a nominal diameter between 5 and 7 mm, in particular <6 mm, are used. With a plurality of such thin suspension ropes, adjustments to the car payload can be carried out more finely. Lubrication and cleaning of thin ropes is also more effective than is the case with thicker ropes. In contrast, with lifts plastic-coated flat strands or a few thick suspension ropes larger gradations to adapt to the load capacity of an elevator a necessary evil. Since undersizing is out of the question for lifts, the ropes will always be oversized, which makes the elevator system more expensive

The invention will be explained in more detail using exemplary embodiments. In the accompanying drawing:

Fig. La is a schematic representation of a cable drive with double wrap in the

Side view and Fig. Lb in plan view,

2 shows an example of a shaft head installation and 2: 1 suspension,

3 shows an example of a shaft wall installation and 2: 1 suspension,

Fig. 4 shows an example of a car floor installation and 2: 1 suspension and

Fig. 5 shows an example of a car roof installation and 2: 1 suspension.

In Fig. 1 a known rope drive with double wrap is shown in more detail. A set of suspension ropes 1, consisting in the example of 8 suspension ropes running in parallel with a nominal diameter of 6 mm, is guided from below via a traction sheave 2 with a nominal diameter of 240 mm and semicircular grooves 4 to a counter pulley 3 with a nominal diameter of 240 mm as well, loops around the counter pulley 3, runs back to the traction sheave 2, wraps around the traction sheave 2, runs back to the counter pulley 3 and is guided downwards again via the latter. Instead of a traction sheave with a nominal diameter of 240 mm, those with a small nominal diameter can also be used. For example, the nominal diameter can only be 180 mm, which corresponds to a ratio of traction sheave diameter to nominal diameter of the support cables of 30. In Fig. La only one of the 8 suspension cables of the suspension cable set 1 is shown for a better overview. Traction sheave 2 and counter pulley 3 are shown arranged horizontally to one another. They can also be arranged perpendicular to one another. The distance between the counter disc 3 and the traction sheave 2 is selected such that, with a horizontal disc arrangement in the shaft head, the suspension cable set 1 runs outside the car sides not shown in FIG. 1. This eliminates the need for an additional deflection plate.

From Fig. Lb it can be seen that the counter pulley 3 is offset to the traction sheave 2 by a certain amount, usually by half the center distance of the rope. Traction sheave 2 and counter pulley 3 can be slightly twisted in addition to the perpendicular axes in order to do justice to the spiral-shaped wrap, with the supporting cables alternately resting in the area of the double guide. The cable deflection can be minimized in this way. The support cables run in semicircular grooves of the traction sheave 2, which are adapted to the nominal diameter of the support cables and corresponding grooves of the counter pulley 3. This not only ensures exact cable guidance and a long service life, but also excellent driving ability due to the flat contact. With undercut seat grooves, the suspension ropes would only rest on part of the possible rope surface. This and the wedge effect in the rope seat would result in transverse pressures and deformations.

With a 2: 1 suspension and the usual conditions for the car mass and the head of a passenger elevator, a load rope set of six 6 mm suspension ropes can achieve car payloads of up to 450 kg at car speeds of 1 m / s. However, higher speeds of up to 2 ms or more are also conceivable. For higher payloads, e.g. a 630 kg car payload and a car speed of 1 m / s, about 8 suspension ropes are placed, depending on the breaking strength of the suspension ropes, and for elevator payloads between 800 kg and 1,000 kg 9 to 12 suspension ropes, in turn depending on the breaking strength of the suspension cables.

The breaking strength of the suspension cables depends not only on the nominal diameter of the suspension cables, but also on the material and structure of the suspension cable. The most important technical data, such as tensile strength of the wires, calculated breaking strength and determined breaking strength, are specified by the manufacturer in a factory certificate and are used by elevator manufacturers to calculate of the necessary number of suspension cables of the suspension cable set 1. The above information can therefore only be used as a guide, especially since a high safety factor, which depends on the nominal cable speed and the cable routing, has a significant influence on the result.

In Fig. 2 an example of a machine room-less installation of the traction sheave drive in the shaft head is shown schematically. The shaft wall 5 delimits the free shaft space. From above you can see the roof of the car 6. Above the car 6 the traction sheave drive with the drive motor 7, the traction sheave 2 with a corresponding nominal diameter of approximately 240 mm and the counter disc 3 with a nominal diameter of approximately 240 mm is installed in the shaft head in such a way that that the traction sheave 2 double wrap suspension cable set 1 with its 6 mm suspension cables runs past the side walls of the car 6 directly downwards, one end of the suspension cable set 1 wrapping two deflection pulleys 8, 9, which are fastened to the floor of the car as a "bottom block" and runs up to a first rope stop 10 and the other end of the suspension rope set 1 wraps around a deflection pulley 12 installed on the counterweight 11 and then runs up to a second rope stop 13. The counterweight 11 and its deflection pulley 12 run laterally between the shaft wall 5 and a side wall of the car 6. The cable guide, with which a 2: 1 ratio of the cable speed on the traction sheave 2 to the car speed with halved driving torque, is used, uses a small one , faster running drive motor 7 with a small traction sheave 2 and thin support cables and is shown again schematically separately. The fasteners for the traction sheave drive in the shaft head are omitted, as are the side guide rails for the car and other components of a conventional cable elevator.

If the traction sheave drive is installed in a shaft pit instead of in a shaft head, two additional deflection rollers are necessary, which increases the number of bending changes of the supporting cables and reduces their cable service life. In the case of reconstructions, however, you will hardly be able to do without such a solution due to the structural conditions. 3 shows the installation of a traction sheave drive on a shaft wall 5. In this example, the traction sheave 2 and the counter pulley 3 are arranged with one another in the extended space for the counterweight 11. The set of suspension cables 1 runs from a first rope stop 10 over the deflection rollers 8, 9 to the traction sheave drive 3, 2, wraps around the traction sheave 2 driven by the drive motor 7, runs to the deflection roller 12, on which the counterweight 11 is suspended, and ultimately runs to the second Rope stop 13. The deflection rollers 8, 9 can be fastened both on the roof of the car 6 and under the floor of the car 6. Both variants are shown schematically. The suspension cable guide described implements a 2: 1 suspension.

If the traction sheave drive is permanently installed in the shaft at the top, bottom or side, it is expedient to fasten it to the elevator frame.

In Fig. 4 the traction sheave drive is installed on the floor of the car 6. The set of suspension ropes 1 runs from the first rope stop 10 around the counter pulley 3 and the traction sheave 2, both of which are fastened to the bottom of the car 6, further upward, via a deflection roller 14, wraps around the deflection roller 12 on the counterweight and is ultimately with the second end attached to the second rope stop 13. Again, a 2: 1 suspension is implemented.

5, the traction sheave drive is installed on the roof of the car 6. The cable guide corresponds to the cable guide according to Fig. 4. Decisive for the choice of the installation of the traction sheave drive on the car floor or on the car roof are ultimately the local conditions in the shaft and the possibilities for easy maintenance of the traction sheave drive.

If the traction sheave drive is installed on the car 6, the car frame or the car main carrier is expediently supplemented by appropriate holding means.

The car can be suspended in a ratio of 1: 1, 2: 1 or 4: 1, depending on whether and how much loose rollers are used. Single-layer round strand cables can be used as supporting cables, the individual round wires being drawn from unalloyed steel with a relatively large carbon content of 0.4% to 1%. However, multi-layer round strand cables can also be used. Furthermore, suspension ropes made of plastic wires or steel and plastic wires can be used. A preferred plastic, because it is highly tear-resistant, is aramid, for example.

In a preferred embodiment of the invention, the support cables have a nominal diameter of 6 mm, which enables traction sheave diameters of 240 mm and smaller.

To further reduce the size of the traction sheave drive and to increase its service life, if in a further embodiment the motor of the traction sheave drive itself is designed without a mechanical double emergency brake device and a double emergency brake device is arranged on the car 6 for this purpose, which has at least one guide rail on both sides for the car 6 acts. The double emergency stop brake device is then preferably a two-disc caliper brake. According to a further preferred embodiment, the electric motor is designed as a converter-controlled three-phase synchronous or three-phase asynchronous motor.

reference numeral

1 set of suspension cables

2 traction sheave

3 counter disc

4 semicircular grooves

5 shaft wall

6 car

7 drive motor

8 deflection disc

9 deflection disc

10 rope stop

11 counterweight

12 deflection disc

13 rope stop

14 deflection disc

Claims

claims

1. Gearless cable elevator with a traction sheave drive with a double pulley (3), a car (6), guide rails for the car (6) and a counterweight (11), in particular for a machine room-less installation, characterized in that the Support cables run in semicircular drive grooves and the ratio of the drive pulley diameter to the nominal diameter of the support cables is <40.

2. Gearless cable elevator according to claim 1, characterized in that the ratio of the traction sheave diameter to the nominal diameter of the supporting cables is essentially 30.

3. Gearless cable elevator according to claim 1 or 2, characterized in that the driving grooves are undercut.

4. Gearless cable elevator according to claim 1 or 2, characterized in that the driving grooves have a slight undercut, preferably an undercut of 1 to 3 mm.

5. Gearless cable elevator according to one of the preceding claims, characterized in that the supporting cables have a nominal diameter between 5 to 7 mm, in particular <6 mm.

6. Gearless cable lift according to one of claims 1 to 4, characterized in that it is configured for car payloads of up to 2,000 kg and has suspension ropes with a nominal diameter of substantially 7 mm, the ratio of the traction sheave diameter to the nominal diameter of the suspension ropes preferably approx 34 is.

7. Gearless cable elevator according to one of claims 1 to 5, characterized in that it is configured for car payloads up to 2,000 kg, in particular between 300 kg and 1,000 kg.

8. Gearless cable elevator according to one of the preceding claims, characterized in that the counter disc (3) is also a spacing deflecting disc.

9. Gearless cable elevator according to one of the preceding claims, characterized in that only the number of support cables placed in the traction sheave drive can be changed to adapt to the cable forces occurring.

10. Gearless cable elevator according to one of the preceding claims, characterized in that the traction sheave (2) and the counter plate (3) of the traction sheave drive are arranged horizontally to one another and in the region of the shaft head or in the region of the shaft pit.

11. Gearless cable elevator according to one of claims 1 to 9, characterized in that the traction sheave (2) and the counter plate (3) of the traction sheave drive are arranged perpendicular to one another and in the region of the extended counterweight space in the shaft.

12. Gearless cable elevator according to one of claims 1 to 9, characterized in that the traction sheave (2) and the counter plate (3) of the traction sheave drive are attached to the floor or roof of the car (6).

13. Gearless cable elevator according to one of claims 1 to 11, characterized in that the traction sheave drive is attached to the elevator frame.

14. Gearless cable elevator according to claim 12, characterized in that the

Retaining elements for the traction sheave drive are integrated in the car frame or car main carrier.

15. Gearless cable elevator according to at least one of the preceding claims, characterized in that a car suspension takes place in a ratio of 1: 1.

16. Gearless cable elevator according to one of the preceding claims, characterized in that a loose-roller car suspension is carried out in a ratio of 2: 1 or 4: 1.

17. Gearless rope elevator according to one of the preceding claims, characterized in that the supporting ropes are steel ropes, preferably single-ply round strand ropes.

18. Gearless cable elevator according to one of the preceding claims, characterized in that the motor of the traction sheave drive is a three-phase asynchronous or three-phase synchronous motor.

19. Gearless cable elevator according to one of the preceding claims, characterized in that the motor of the traction sheave drive is designed without a mechanical emergency stop braking device.

20. Gearless cable elevator according to one of the preceding claims, characterized in that a double brake is arranged on the car (6) as an emergency stop braking device, which acts on both sides of at least one guide rail for the car (6).

21. Gearless cable elevator according to claim 20, characterized in that the

Braking device is a two-disc caliper brake.