HK1156291B - Catch device with an energy accumulator element - Google Patents

Description

The present invention relates to a fishing device which is, for example, part of a safety device for a lifting device, where the fishing device is used to attach a lifting cabin to a guide rail, a safety device with a corresponding safety device, a lifting device with a corresponding safety device and a method for operating a fishing device in accordance with the invention.

A lifting device normally comprises a lifting cab and at least one counterweight, which are moved in a counterbalance shaft. The lifting cab and at least one counterweight are moved in and along guide rails. For safety reasons, a lifting device is usually equipped with a catching device which is part of a safety device. The catching device attaches to the guide rails of the lifting cab and/or counterweight. The speed of movement of the lifting cab or counterweight is thereby slowed or reduced to zero by fixing the catching device on the guide rail. The brake is released or fixed by a speed limiting direction, which limits the speed of the lifting cab or counterweight and exceeds the weight of the lifting cab.

This speed limitation is achieved, for example, as shown in patent application EP-B1-1 298 083, by coupling the lifting cab or counterweight by means of a bar and lever with a speed limiter limiting rope. The limiting rope is passed in the shaft head over a speed limiter rope panel and in the shaft pit over a winding coil. During the ride the lifting cable drives the limiting cable, the speed of the lifting cable is monitored by the speed limiter via the limiting cable. When the lifting cable is overspeed, the speed limiter blocks the speed limiter, with the lifting cable moving over the rope panel in the direction of the lifting cable and the rope limiter moving back towards the catching cable.This in turn keeps one or two wedge-shaped and roller-mounted brake blocks of the catching device in a first (friction) contact position with the guide rail. This in turn activates a spring column made of plate springs, which is placed opposite the brake blocks in a pincer-shaped double-lever design. This ensures that the traction force in the catching and leverage is not the one actually braking but only the one generating the catching direction. The effective force is generated by the brake brake. This is also true for the functional balance of the brake cable. For example, the electronic monitoring of the catching and electromagnetic radiation can also be obtained from the opposite direction.The traditional mechanical speed limiter and the traditional limiting rope are not used in this latter variant.

A safety device with a similarly designed catching device is shown in US-2,581,297, where the braking force is generated by a spiral spring.

However, these known fishing gear have the following disadvantages: The force storage element,whether a spring column made of individual plate springs as in EP-B1-1 298 083 or a spiral spring as in US-2,581,297, has no safety reserve.A failure of this single force storage element results in a failure of the catching device.There are countries whose safety regulations require a safety reserve for safety-relevant parts in lifting equipment that would not be met by the known catching devices.The functioning of the catching device can be optimized in terms of both material saving,braking power flow and thus the delay experienced by lifting operators in the lifting cabin.

The disadvantages described above can be eliminated according to the invention by arranging at least two force storage elements between the different force storage elements on the one hand and by optimizing the overall course of the force path characteristic on the other. Furthermore, it is consistent with the invention to select the force storage elements in such a way that their individual characteristics complement each other in a certain way. Furthermore, the invention states that when a catching device is designed in accordance with the invention, the outer diameter of the force storage elements is arranged across a disc. This disc, after a certain degree of pressure of the first, is obviously weaker, means a weaker force, the frontal force of a single element can be reduced by a small weight loss and the direction of the compression is more favourable. This is achieved by automatically moving the force across the entire disc (as in the case of the two components), and only because the force is not yet at its maximum potential and the maximum force is not yet at its maximum.

All types of springs can be considered as force storage elements, in particular plate springs, which can be assembled in series or in parallel to form so-called spring columns, but also screw-top, spiral, sheet or gas pressure springs (generally pneumatic) or hydraulic (e.g. valve chamber springs) or combinations of all the above types of springs.

The disc springs have a degressive characteristic, i.e. the spring rate (spring constant, force storage rate) decreases exponentially with increasing springing. According to the invention, such disc springs or force storage elements are preferred, which have a progressive characteristic (exponentially increasing spring rate).

The resulting characteristic line of the force storage device composite may be unstable, i.e. from the point at which the front edge of the cylindrical housing hits the disc and thus stops further compression of the first, weaker force storage device, a sudden drop or even an increase in the brake force value of the catching device may occur.

However, regardless of whether the overall characteristic line is unstable or steady, the ratio of the power storage elements can be chosen in such a way that only the first, weaker power storage element is used, for example, in the event of a faulty steering. The second, stronger element, on the other hand, is used only, for example, in the event of a failure of a load-bearing equipment - and the associated higher forces.

The continuity of the overall characteristic can be technically achieved by the second force storage element having such a high spring rate that only from the moment the front edge of the cylindrical housing hits the disc, a compression of this force storage element is possible. In other words, the absolute amount of the absorbed compression force - and the resulting recoil force - with which the first force storage element exits is identical to the input value of the second force storage element.

The cylindrical housing, on the other hand, can be optionally formed from a disc and a tube. The disc can be identical to the disc that separates the two force storage elements for cost reasons. The cylindrical housing or tube, on the other hand, can surround the force storage element externally, but also be formed internally as a distance shell.

A further preferred design of a catching device according to the invention includes a pre-tensioning device for the force storage elements. This may be, for example, realized in a simple and well-known way by means of a screw in a threaded sleeve arranged on a spring bolt so that the rotations of the screw compress or decompress the force storage elements which are mounted on the spring bolt. This known pre-tensioning device, however, in connection with the arrangement according to the invention, involves at least one weaker and one stronger force storage element, so that movements of the pre-tensioning device only or predominantly re-heat the weaker force storage element. A pre-tensioning element for the second, more powerful lifting force element, insofar as possible, increases the force storage elements separately. If we have a pre-tensioning element, we will not first apply it to the first working element, but to the second, and then to the first, if possible, if we have a maximum of the force transferring elements.

However, in order to be able to foreclose the second, stronger force storage element, a further preferred design of a catching device according to the invention provides for a spring bolt with different external diameters and thus strokes. With a corresponding foreclose device which separately holds and tensiones only the second, stronger force storage element, a desired amount of foreclosure can then be achieved exclusively for this second, stronger force storage element, for example by using spacers. These spacers are exposed to the impact after the spring is released. The spacers or the attachment parts are, however, not necessarily invulnerable to the pressure of the spring. The compression of the forward force components can be carefully limited by their reversal of the direction of the spring, which can be controlled by means of a safe and secure means of a counter-pressure.

The first, weaker force storage element is then, after the second, stronger force storage element has been pre-tensioned in the manner described above, known to be actuated by the screw which holds the spring bolts.

The spring bolt may also be designed, as an option, to have a continuous, identical outer diameter but to provide resting positions for the disc into which the latter can be fitted with a bayonet-like fastener.

The axial adjustability of the disc along the longitudinal axis of the spring bolt, or/and also adjustability in the same direction of the cylindrical housing, leads to a further design variant of the invention of a catching device, in which the distance between the cylindrical housing and the disc can be adjusted, which allows - optionally in addition to the pre-tensioning by the screw described above - to adjust the lift of the first force storage element.

A further design variant according to the invention provides for three different force storage elements. For the separate, prior pre-tensioning of the two stronger force storage elements, the corresponding pre-tensioning devices may be provided as an option and a spring bolt, which then forms three different outer diameters.

The device of the invention produces the braking force preferably by means of a so-called spring column, which is made up of individual spring springs arranged on the spring bolt. The spring springs may be arranged in a row or parallel or in two or three-row arrangement in a row or parallel. The individual spring springs are preferably made of non-rust and hot-resistant spring steels. Examples include copper (CuSn 8, CuBe 2) and nickel alloys (Nimonic, Inconel, Duratherm) or chromium-vanadium alloys or also porcelain. In general, the shrinkage springs of group 2 of DIN 2093 are different, but the use of the spring springs is more common, for example, in the case of a group of materials, and the strengthening of the material is also achieved by using a combination of at least three materials.

As mentioned at the outset, a catching device of the invention may be located both on the lifting cab and on the counterweight, and the catching device may be located, for example, on the bottom of the lifting cab or on the counterweight itself, but also on the top of the lifting cab.

The above described gear has the advantage over gear acting on the support itself of always being able to safely brake independently of any break in the support or wherever the support breaks.

Other advantages of a catching device of the invention are improved hysteresis properties and easier disassembly when the catching device is removed after use or repair or maintenance work by re-dividing a path area into two or more path areas.

A catching device of the invention can also be fitted to tilting lifts, drills, shelf controls and other equipment for transporting persons or material. It is also suitable not only for the interception of downward movements of the lift cabin but also for upward movements which may be caused, for example, by faulty controls. For this purpose, a catching device of the invention can also be fixed to the roof of the lift cabin by rotating it 180 degrees, optionally in addition to the mounting types and mounting locations disclosed so far.

The present application discloses at least two force storage elements connected in series, such as spring columns made of plate springs, which are arranged on a bolt. However, the principle of the invention can also be realized with force storage elements wrapped around each other. For example, the weaker or stronger force storage element may have an inner diameter that accommodates the other force storage element.

Further or advantageous designs of the fishing gear or lifting device according to the invention are the subject of the dependent claims.

The list of references is part of the revelation.

Figures are used to illustrate the invention in a symbolic and illustrative manner.

The figures are described in a coherent and comprehensive manner: identical reference marks mean identical components, reference marks with different indices indicate identical or similar components.

It shows Fig. 1 a schematic representation of a lifting device with a safety device with a catch device corresponding to the state of the art;Fig. 2 a schematic representation of a catch device corresponding to the state of the art;Fig. 3 a schematic representation of a part of a catch device according to the invention;Fig. 3a a preferred design variant of the catch device according to the invention from Fig. 3 at the time of installation;Fig. 3b a sickle-shaped disc;Fig. 4a a representation of a cumulative overall characteristic line of the catch device with a continuous linear flow with a constant and widely varying forceFig. 3 a schematic representation of the characteristic line of the catch deviceFig. 4 a schematic representation of the characteristic line of the catch deviceFig. 5a a schematic representation of the characteristic line of the catch deviceFig. 5a a schematic representation of the characteristic line of the catch device with a constant and widely varying forceFig. 5a a schematic representation of the characteristic line of the catch deviceFig. 5a a schematic representation of the characteristic line of the catch device with a continuous forceFig. 5a a schematic representation of the characteristic line of the catch device with a continuous forceFig. 5a a schematic representation of the characteristic line of the catch element; 5a a representation of the characteristic line of the catch element; 5a and a progressive representation of the characteristic line of the catch element;Fig. 5a a schematic representation of the characteristic line of the catch element; 5a; 5a a progressive representation of the characteristic line of the catch element; 5a; 5a representation of the characteristic line of the catch element; 5a; a progressive characteristic characteristic line of the characteristic line of the catch element; a characteristic line with a characteristic of the characteristic force; 5a representation of the characteristic of the characteristic force; 5a characteristic of the characteristic of the characteristic force; 5a characteristic of the characteristic of the characteristic force; a characteristic of the characteristic

Fig. 1 shows a lifting device 100 with a lifting cabin 2 which can be operated in a lift shaft 1 and which is connected to a counterweight 4 via a support device 3 by means of a support device 3. The support device 3 is driven by a drive drive 5 of a drive unit 6 when in operation. The lifting device 2 and the counterweight 4 are guided by means of guide rails 7a and 7b extending over the shaft height. The lifting device has an upper floor with an upper floor door 8, a second upper floor with a second upper floor door 9, another floor with additional floor doors 10 and a lower floor with a lower floor door 11. At a height of 15 feet, the drive unit 6 and a 13 speed accompanist are arranged at different speeds, with two sets of 15 and 14 double-deck elevators, one on each side of the lifting device.

In addition, the double lever 14a is connected to a limiting rope 19 of the speed limiter 13 fixed; the limiting rope 19 is guided in the shaft head 12 via a rope disc 58 of the speed limiter 13 and in a shaft pit 20 via a rolling roller 21; during the journey the lift cab 2 drives the limiting rope 19 and the speed of the lift cab 2 is monitored via limiting rope 19 from the speed limiter 13.

At overspeed of the lifting cab 2 the speed limiter 13 blocks the rope disc 58 with the lifting cab 2 dragging the limiter 19 over the rope disc 58. By friction at the rope disc 58 the limiter 19 exerts a pull on the double lever 14a in the direction of the arrow 26 upwards. When this is done, the double lever 14a turns around a pivot point 15a. This transfers, on the one hand, a pull upwards over the bars 17a to a catching device 16a. However, on the other hand, if the lifting device 100 is fitted with a second one, coupled to the first catching device 16a, as shown, in a preferred configuration, the second one is equipped with a second catching device 16b,In addition, the double lever 14a, by means of a fixed angle of approximately 90 degrees, at its apex at the pivot point 15a, directed to the lifting cab 2, applies a pressure movement to a connecting rod 18. This connecting rod 18 in turn applies pressure to the second double lever 14b, which, like the first double lever 14a, is formed by a fixed angle of approximately 90 degrees, at its apex at the pivot point 15b, directed to the lifting cab 2. The pressure of the connecting rod 18 thus creates a bending of the double 14b, which is in turn transferred to the second lifting device 16 by a 17 step pull.

The safety device 200 shown thus comprises the speed limiter 13 and at least a double lever 14 which, by means of the lever 17, triggers the tractor 16 by a pulling force.

The endless limiting rope 19 is tensioned by means of the rolling coil 21 located in the shaft pit 20, with a roller axle bearing 22 at one end pointed at a pivot point 23 and supporting a tensioning weight 24 at the other end.

Fig. 2 shows a diagram of a catch device 16 corresponding to the current state of the art. A force storage element 27 is formed as a spring column by placing a pair of plate springs 34 in a row and pairs of plate springs formed in this way are then in parallel on a bolt 33 with a longitudinal axis 55. The force storage element 27 is tensioned by means of a pre-tensioning screw 35 in a thread box 36 and a disc 37. The bolt 33 is contained in axes 32a, 32b of brake levers 29a, 29b, the latter being placed as symmetrical pressure pressures in a rotor 31a, 31b and equipped as a double-sprung heater.

The brake blocks 28a and 28b are, as is not apparent from this view, wedge-shaped and each is contained in a roll cage 39a and 39b. This results in the tractive or compressive force of the bar 17 described in Figure 1 being sufficient merely as a triggering, stimulating force for the catching device 16 by holding one or both of the brake blocks in a starting brake position. The actual brake force F of the force storage element 27 - as a spring-supported response to its compression according to Hooke's law - then builds up automatically due to the friction of the brake block 28 on the guide rail 7 and due to the brake block 28's wedge.

Figure 3 shows a schematic representation of a device 16c according to the invention in a cross-sectional diagram. Unlike the device 16 shown in Figure 2, it does not have a single single-stage force storage device 27 but a force storage device composite 30 composed of a first force storage device 27a and a second force storage device 27b. The first force storage device 27a is a spring column of plate springs 34 which are arranged in pairs of plate springs parallel to the bolt 33.

The second force storage element 27b forms a spring column of spring plates 34 which are arranged as several serial threes in parallel on the bolt 33. However, the invention includes a wide variety of spring plate assemblies, whether in series or parallel or also a wide variety of spring storage elements. This means that other types of springs, such as spiral, sheet, screw-top or gas pressure spring or combinations thereof, are also considered. According to the invention, the force storage element composition 30 is composed of two or more spring storage elements 27 which differ in terms of the type of the invention and their characteristics and/or spring line.

The first force storage element 27a is compressed by a cylindrical housing 40; after a defined degree of compression of this force storage element 27a, a front edge 41 of the cylindrical housing 40 presses on a disc 37a located between the force storage elements 27a and 27b. This results in an increase in the compression of the first force storage element 27a and an exclusive compression of the second force storage element 27b, which here, as shown, has more and stronger plate-fed packages than the force storage element 27a and thus also a higher spring rate.

Another design variant, not shown in detail in this figure but still in accordance with the invention, provides, in addition to the one described above, an adjustment of the maximum compression of the first, weaker power storage element 27a by adjusting a distance 42 between the front edge 41 of the cylindrical housing 40 and the disc 37a. This can be done independently of the pre-tensioning by means of the screw 35 in the thread casing 36 with a further thread adjustment for the cylindrical housing 40. Another adjustment of the distance 42 may consist in the disc 37a being connected to the cylindrical power storage element by means of adjustable rotational positions so that a compression force of the power element 42 is equal to or greater than the value of the current of the 27a after a pre-tensioning of the 42a is achieved, but not beyond the value of the zero value of the 42a.

Both the known advance voltage by means of the screw 35 as shown in Fig. 2 and the adjustment of the cylindrical housing 40 described above, due to the fact that the catching device 16c of the invention has a weaker force storage element 27a and a stronger force storage element 27b, act exclusively or predominantly on the weaker force storage element. In other words, the stronger force storage element 27b can no longer be advanced without skipping the earlier and more attractive working area of the first force storage element 27a.

To overcome this disadvantage, a further and preferred design of a catching device according to the invention provides for the adjustability of disc 37a. This adjustability is designed according to the invention so that disc 37a cannot move to the left, to the weaker force storage element 27a, beyond defined and adjustable end positions. To the right, to the axis 32b, however, disc 37a follows unimpeded the pressure of a front face 44 of an outer plate spring package 43 of the force storage element 27a or - depending on the interpretation of the spring difference between the force storage element 27a and the force storage element 27b - the pressure expansion of the front element 41a. However, the second expansion can be achieved by means of a compression expansion, which is described as the maximum pressure expansion of the front element 37a.

Figures 3a and 3b show how the inventive feature of the separate tensile strength of the stronger power storage element 27b can be technically realised. The bolt 33a has a smaller diameter along the extension of the power storage element 27b than along the extension of the power storage element 27a and thus forms a connection 47 to the disc 37a. By means of a tension device 48 applied to the disc 37a and the axis 32b, as shown on the disc 37a and a bolt 46 respectively, the bolt 46 can be brought to the desired size when the second power storage element 27b is installed and additional bolt 45m thickness can be inserted to the desired size. This bolt has a larger thickness than the first bolt 37a and can be removed by means of a small force or bolt 45a. This is due to the fact that the first bolt 37a is designed to be more resistant to the pressure of the second bolt 27a and the bolt 27a is designed to be more resistant to the pressure of the second bolt 27a.

Alternatively, the bolt 47 may be shaped by having two parts which can be screwed on, in which case the panels 45 need not be shaped like a sickle, but may be filled like the panels 37a, which may be advantageous in terms of absorbing the shear forces in panels 37a and 45.

The order of arrangement shown in Figures 3 and 3a, with a central weaker force storage element 27a and an external stronger force storage element 27b, is an example; it may also be the other way round, experimental experiments and practice will show whether it is advantageous, for example, if the central stronger force storage element 27b is arranged and thus more or less independently describes the compression motions of the weaker force storage element 27a; it is also conceivable that an arrangement of the cylindrical housing 40 at the outer edge would be as stable as possible to one of the 32 axes. For example, a ring of 49 axes, with 40 axes, could be directly attached to the 32 axes.

Figures 4 and 4 show an example of the characteristic composition of the power storage device composite 30, i.e. the individual characteristics of the first power storage device 27a and the second power storage device 27b as shown in Figure 3.

In Fig. 4a, it is first seen that a path s (compression) equal to zero does not correspond to a pressure force F equal to zero. This initial force, which is needed to stimulate a spring, is generally called the breaking force.

The characteristic line of the force storage element 27a assigns to each increasing value for the path s an increasing value for the compressive force F. It is therefore in itself constant. In addition, it is progressive, i.e. the compressive force increases not only linearly but in an over-proportional (exponentially) increasing ratio.

The dashed line continuing the line of the force storage element 27a shows how the force storage element would continue to behave if not at point S1 the front edge 41 of the cylindrical housing 40 did not hit disc 37a. The dashed line of the stronger force storage element 27b is also in itself steady and progressive and would, without the advance of the weaker force storage element 27a, start with a higher compressive force along the dashed path to point S1. From point S1, which corresponds to the contact of the front edge 41 with disc 37a, the compressive force F falls to a lower value than just before. The entire dashed line for the somewhat richer force storage element 30 is uncomposite.

Figure 4b shows, on the other hand, a continuous course of the entire characteristic line of a force storage element composite 30'. This can be achieved, as shown, by crossing a characteristic line 27a' and a characteristic line 27b'. This in turn would mean that, even before the cylindrical housing 40 finishes the working range of a first power storage element 27a', a second power storage element 27b' starts its work. The result is a common working range S2-S1.

However, the continuous characteristic can also be achieved by the second force storage element 27b' seamlessly starting where the second force storage element 27a' ends, i.e. the force storage elements are so precisely aligned with each other by their spring rates that when the compression of the first force storage element 27a' by the cylindrical housing 40 is completed, the second force storage element 27b' takes on the same amount of force.

Err1:Expecting ',' delimiter: line 1 column 122 (char 121)

Fig. 5 shows schematically in a cross-sectional representation another design of a fishing device 16e according to the invention. In this design, the force storage element composite 30a is formed from a first force storage element 27a, a second force storage element 27b and a third force storage element 27c. As can be seen from the symbolic representation and arrangement of the plate springs 34, they form with pairs made of one plate spring 34 each, the first, weakest force storage element 27a. The second, middle, more powerful force storage element 27b is made of a double and the third, richer, strongest force storage element 27c is made of three triple-anode elements.

Unlike the cylindrical housing described in Figure 3, cylindrical housing 40 does not directly meet disc 37a, but for the time being another cylindrical housing 40a, which surrounds the second force storage element 27b.

The force-path is thus cascading and according to the invention in one of the modes shown in Figures 4, individually or in combination, but only extended by one further step.

Fig. 5a shows in a cross-sectional diagram a further design of a fishing device 16f according to the invention. In this design, the force storage composite 30b is formed from a first force storage element 27d, a second force storage element 27e and a third force storage element 27f. As can be seen from the symbolic representation and arrangement of the respective plate springs 34a-34c, the force storage element 27d is the weakest because it is formed from the smallest and thinnest plate springs 34a. The force storage element 27f is the strongest because the individual plates 34c are the largest and thickest respectively and at the same time in three-dimensional order.

The arrangement of these three force storage elements 27d-27f is arbitrary. For example, in this design variant the weakest force storage element 27d is shown to be located at axis 32b or at ring 49b. The ring 49b also forms the cylindrical housing 40b surrounding the first force storage element 27d.

From a certain compression level of the force storage element 27d, the front edge 41b of the cylindrical housing 40b presses on the cylindrical housing 40c surrounding the second, middle force storage element 27e, thereby suspending the compression of the first, weakest force storage element 27d and starting again, depending on the interpretation of the difference in spring rate between the first force storage element 27d and the second force storage element 27e, or depending on whether the working areas of the force storage elements 27d and 27e are desired to overlap, now or only before the second force storage element 27e is compressed.

The capture device 16f shown herein also has bolts 33b, which have a different diameter for each individual force storage element 27d-f. In this way, it is possible to obtain a pre-tensioning for those force storage elements (27e and 27f) with appropriate clamping devices and the selection of a corresponding thickness of a housing wall 50 of the cylindrical housing 40c or a corresponding thickness of the disc 37a, which are stronger than the weakest force storage element 27d.

As already described in Fig. 3, the state-of-the-art pre-tensioning device 36 by means of the screw 35 (see here) which acts on the whole composite 30b force storage element would only or mainly pre-tension the weakest 27d force storage element. This known pre-tensioning device 36 shown in Fig. 3 is no longer shown in the present Fig. 5a, but it may be represented on the axis 32b opposite the bolt 33b. In any case, its presence makes it clear that each of the three 27d-27f force storage elements, even the weakest 27d force storage element, can be pre-tensioned.

As shown by the possible characteristics of the individual force storage elements, they may be so designed that the weakest force storage element 27d describes its maximum path first and only then the spring rate of the second force storage element 27e allows compression or force absorption. However, if this is not the case and, as shown, the force storage element consists of plate springs, when the first force storage element 27d is compressed and compression of the second medium force storage element 27e is also simultaneously applied (overlapping characteristics, for example, as in Figure 4b), the widest plate spring 34a or the first or subsequent spring springs T may be the first to be compressed or force absorbed, in the sense that they cannot fall out of the range between a possible gap of 51a and 51a, as described above, and that they may fall out of the range of 50a, as described above, with a slightly sloping area between the head and the head, which is not possible to remove, as in the case of the 51a and 51a, as described above.

In any case, it is essential that the weakest force storage element 27d be associated with the largest and strongest force storage element 27f, the smallest diameter of the bolt 33b, otherwise the paths of the force storage elements 27 will be blocked by the shocks 47.

Figure 5b shows a further design variant of a catching device 16g, which has a bolt 33c with 52 nut profiles extending along the longitudinal axis 55; between them, there are stud profiles 53 which, with an outer edge 56 still correspond to an outer diameter 0 of the bolt 33c. On this outer edge 56 the plate spring 34a is still carried, although the disc 37b and a distance of the shell 57 (the cylindrical case 40 is shown as a disc and a shell in this design) move to the left 27 due to the compression of the central force storage element. An analogous formation, with only lower 52a nut profiles, a middle force element 27 is provided between the strongest force element 27 and the strongest force element 27 is provided.

Figure 5c shows a cross section along the cutting axis A-A from Figure 5b. The disc 37b forms along its respective internal diameter at least two, preferably four almost diametrically opposite, segments 54 running along the respective nut profile 52. The rear front face of the segment 54 is therefore the surface to the respective contact point 47a and 47b, which in this configuration is no longer fully formed but only to a certain percentage of the total circumference. This further inventive design of the bolt 33c with stepped profiles 53, 52a and 52a and running segments 54a in Figure 5a has the advantage that the lower part of the bolt is protected against the forces of the graying of the solution.

The features of the invention described in Figures 3 to 5 can be combined, although only for the design variant shown, for example the combination of characteristics shown in Figures 4 which was shown there only in connection with a first and a second force storage element according to Figure 3 is also optional for the second and third force storage element according to Figure 5 and the adjustment of the distance 42 described in connection with Figure 3 can be easily achieved in connection with the design variant according to Figure 5.

List of reference marks

- elevator shaft2 - elevator cabin3 - supporting elements4 - counterweight5 - drive shaft6 - drive unit7 - guide rail8 - top floor door9 - top floor door10 - further floor door11 - bottom floor door12 - shaft head13 - speed limiter14a, 14b - double lever15a, 15b - pivot point16, 16a - catching device17a, 17b - barrel18 - connecting rods19 - limiter rope20 - shaft pit21 - shifting coil22 - wheel axle storage23 - pivot point24 - spindle weight25 - buffer26 - train direction from 1927 - richer element27a, 27-33b - weight lifting force element27a, 27-33b - weight lifting force element27c - weight lifting force element27a, 27-37a, 27-37a, 27-37a, 27-37a, 27-38a, 27-38a, 27-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a, 30-38a-32, 30-38a-32, 30-38a-32, 30-38, 30-38, 30-38, 30-38, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 30-34, 3037a-37c - disc 38a, 38b - brake liner39a, 39b - roller cage40, 40a-40c - cylindrical housing, outer or inner casing, road delimitation41, 41a-41c - forehead edge of 4042 - distance between 41 and 37a43 - outer plate spring package of 27a44 - forehead surface of 4345 - sickle-shaped disc46 - bolt end47, 47a, 47b - attachment 48 - clamping device49a, 49b - ring50 - pressure wall51a, 51b - distance52, 52a - axle profile53 - step profile54, 54a - segment of the seat55 - length of 3356 - circumference or side of the road - distance of 3757a - distance of the seat - lifting force - direction of the road - safety force - direction of the road - direction of the vehicle - direction of the road - direction of the vehicle - direction of the vehicle - direction of the road - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - direction of the vehicle - vehicle - vehicle

Claims (15)

1. Safety brake device (16) with a force store element (27), which by way of at least one brake lever (29) and at least one brake shoe (28) acting on a guide rail (7) generates a braking force (F) which stops a lift cage (2) and/or a counterweight (4), characterised in that the force store element (27) is a force store element combination (30) consisting of a first store element (27a) and at least one second force store element (27b) and that the force store elements (27) are connected in series and that the force storage rate of the second force store element (27b) is higher than the force storage rate of the first force store element (27a).
2. Safety brake device (16) according to claim 1, characterised in that the force store elements (27) are separated by a washer (37a) at a pin (33) guiding the force store elements (27) and in the case of compression movements of the force store element combination (30) a travel limitation (40) for the first force store element (27a) impinges on the washer (37a).
3. Safety brake device (16) according to claim 2, characterised in that the travel limitation (40) and the washer (37a) form a spacing (42) which is adjustable by means of an axial adjustability of the travel limitation (40) along the longitudinal axis of the pin (33) or by means of an axial adjustability of the washer (37a) along the longitudinal axis of the pin (30) or by means of both capabilities of adjustment.
4. Safety brake device (16) according to claim 2, characterised in that the second force store element (27b) has a characteristic curve which connects at a travel point (s₁) of the force store element combination (30) at which the travel of the first store element (27a) is limited by the travel limitation (40).
5. Safety brake device (16) according to any one of the preceding claims, characterised in that it comprises a first biasing device (36) for the first force store element (27a) and for the second force store element (27b).
6. Safety brake device (16) according to claim 5, characterised in that it comprises a second biasing device (48) exclusively for the at least one force store element (27b) with the higher force storage rate.
7. Safety brake device (16) according to claim 2, characterised in that the pin (33) has different outer diameters and thus abutments (47) for spacer washers (45).
8. Safety brake device (16) according to claim 2, characterised in that the pin (33) has a continuous outer diameter and detent positions at which spacer washers (45) are detentable.
9. Safety device (200) with at least one safety brake device (16) according to any one of the preceding claims 1 to 8.
10. Safety device (200) with at least one safety brake device (16) with at least one force store element (27a) and second force store element (27b) with different force storage rates, characterised in that the force store elements (27) are connected in series and press at least one brake shoe (28) against a brake disc or guide rail (7) by means of at least one brake lever (29), in lift equipment (100) with at least one lift cage (2) which runs along at least one guide rail (7), wherein the safety device (200) comprises at least one speed limiter (13) with a limiter cable (19) and wherein tension forces of the limiter cable (19) are transmissible to the at least one safety brake device (16) at the lift cage (2) so that at least one brake shoe (28) of the safety brake device (16) can be pressed against the guide rail (7) by the force of the first force store element (27a) up to a travel limitation (40) and by the force of the second force store element (27b) from the travel limitation (40).
11. Lift equipment (100) with at least one safety device (200) according to claim 9 or 10.
12. Use of a force store element combination (30) consisting of at least one force store element (27a) and second force store element (27b) with different force storage rates in a safety brake device (16c), wherein the force store elements (27) are connected in series and press at least one brake shoe (28) against a brake disc or guide rail (7) by means of at least one brake lever (29).
13. Method of actuating a safety brake device (16) with at least one force store element (27a) and second force store element (27b) with different force storage rates, wherein the force store elements (27) are connected in series and wherein the force store elements (27) press at least one brake shoe (28) against a brake disc or brake rail (7) by means of at least one brake lever (29), comprising the following steps in the following sequence:

    - triggering the safety brake device by bringing the at least one brake shoe (28) into frictional contact with the brake disc or brake rail (7);

    - pressing at least one brake shoe (28) against the brake disc or the brake rail (7) with the force of the first force store element (27a); and

    - reaching a travel limitation (40) for the first force store element (27a) and thereupon taking the first force store element (27a) out of action and bringing the second force store element (27b) into action.
14. Method according to claim 13, characterised in that the bringing of the at least one brake shoe (28) into frictional contact with the brake disc or brake rail (7) is carried out by the tension of a limiter cable (19), which moves at lower speed than a lift cage (2), of a speed limiter (13) and the safety brake device (16) is thereby triggered.
15. Method according to claim 13, characterised in that the bringing of the at least one brake shoe (28) into frictional contact with the brake disc or brake rail (7) is carried out electromagnetically.