WO2007076937A2

WO2007076937A2 - Emergency lowering device

Info

Publication number: WO2007076937A2
Application number: PCT/EP2006/012337
Authority: WO
Inventors: Alexander Von Gencsy; Hans-Peter Becker
Original assignee: Alexander Von Gencsy; Hans-Peter Becker
Priority date: 2005-12-21
Filing date: 2006-12-20
Publication date: 2007-07-12
Also published as: DE102005061364A1; DE102005061364B4; WO2007076937A3

Abstract

The invention relates to a device for the emergency lowering of loads and/or individuals. Said emergency lowering device (1) comprises a revolving shaft (5) with a cable winder (2) positively coupled thereto. The device comprises at least one hub body (7), said hub body (7) being rotatably enclosed by an outer body (8) and a brake device (6) being interposed between the hub body (7) and the outer body (8).

Description

Emergency lowering device

The present invention relates to a Notabsenkgerät for lowering loads and / or people from high altitudes in emergency situations and / or failure of operated lifting and lowering devices, such as elevators or motorized cranes. Furthermore, the Notabsenkgerät is particularly suitable for self-rescue of people from high altitude, the so-called altitude rescue.

The height rescue of persons makes considerable demands. In addition to rescuing the person from height itself, more aggravating conditions are often added, such as a high-rise fire. Especially with the latter occur in addition to the risk of falling altitude the hazards of fire or flue gases for the person to be rescued added. In particular, in high-rise fires in the relocation of the on-site escape routes, for example by fire or flue gas, an external rescue is necessary.

Known measures for rescue of persons from buildings include ground rescue with ladders or cranes as well as air rescue by helicopter or other aircraft, as described for example in DE 102 51 208. However, these methods have some disadvantages. So the rescue of the ground is generally no longer possible from building heights or whereabouts of the persons to be rescued of more than 40 m above the ground rescue unit. Air rescue is often hindered or made impossible by the flames and the associated buoyancy and the flue gases, especially in building fires. Furthermore, the aforementioned method has in common that they allow the rescue of altitude only after arrival of rescue personnel and rescue equipment. In particular, in emergency situations, in which another form of danger, such as fire or flue gas, the person to be rescued, the associated loss of time can be devastating to the implementation of altitude rescue. The aforementioned time loss is avoided by so-called self-rescue equipment. Thus, DE 80 30 414 U1 describes a Kettenabsprunggerät for self-rescue from heights, in which the rescuing person holds on a holding device or is fixed, wherein the holding device is connected via a cable with a located on the ground chain weight. For self-rescue, the person jumps from a platform, with increasing downward distance by means of the cable chain weight is raised, which slows down the falling speed of the person to be rescued. In this case, the chain weight increases with the distance, in particular by the fact that with increasing distance additional chain strands are attached to the chain weight. The device according to this prior art is basically suitable for self-rescue, but also has considerable disadvantages. Thus, the aforementioned self-rescue system requires a considerable construction effort for installation on a building. Thus, the system has the disadvantage that the weight of the person to be rescued can vary only to a small extent. Too light persons, such as children, are at risk of the chain weight being too large and the person to be rescued not being drained to the ground. In return, there is the danger in heavy people that the chain weight is insufficient and the person to be rescued hits the ground at too high a speed. The latter carries a considerable risk of injury and is to be rejected.

Another problem is the reduction of loads in case of failure of the proposed lifting and lowering devices, especially in emergency situations. The following examples serve only to illustrate the invention. For example, there is the problem with elevators in high-rise buildings that they are fixed in case of failure of their drive device by the known emergency braking systems at the respective place where they are at the time of failure of the drive system. This can be done disadvantageously between two floors, so that leaving the elevator is impossible. When coinciding the failure of the drive device as well as a further hazardous situation, such as a fire, this can lead to a significant threat to the people in the elevator. There is therefore an urgent need for an automatic Notabsenkeinrichtung that is independent of the drive means and to the external interventions, said Emergency lowering simultaneously a controlled lowering, here the passenger car basket, causes and ensures.

Another example of an emergency lowering device that lowers a load in an emergency situation, with simultaneous failure of the proposed lifting and lowering devices, for example, is the lowering of lifeboats on ships. It is obvious that there is a considerable need for self-regulating emergency lowering devices, which can lower the lifeboats from the upper curb to the waterline, with simultaneous failure of the ship's systems and thus the failure of electric or hydraulic winches.

The example made above serve only to illustrate the needs of the emergency lowering device according to the invention and do not represent a limitation to the aforementioned application examples.

Object of the present invention is to overcome the disadvantages of the prior art and to provide an emergency lowering, which is suitable to lower people and / or loads from heights, the emergency lowering independently adjusts a predetermined lowering speed. Another sub-task of the present invention is that the lowering speed is within the application limits independent of the expected loads. Another object of the present invention is to provide a Notabsenkvorrichtung that operates independently of predetermined lifting and lowering devices. It is also a part of the present invention that the emergency lowering is fail-safe.

The objects are achieved according to the technical features of the independent claim. Preferred embodiments are presented in the subclaims.

The present invention is based on an emergency lowering of persons and / or loads by abseiling. According to the invention a device is provided for this purpose, comprising in its simplest embodiment, a cable reel on a revolving axis, wherein the rotating axis with the interposition of a Translation or a transmission with an inhibitor is connected.

Optionally, the device may be fixedly attached to the building, ship or the like, wherein the abzusenkende load or person, hereinafter referred to simply called load, be discharged by means of the free cable end of the cable located on the rope reel or the device fixed to the load to be dropped, such as a Lifeboat or elevator be installed, in the latter embodiment, the rope end is then attached to the building or the like. The aforesaid attachment is hereinafter referred to as an anchor point for purposes of description.

Suitably, the free end of the rope is either provided with a coupling device or fixedly connected to the anchor point. A suitable coupling device may for example be a snap hook or the like. Said coupling device is particularly advantageous if the load to be lowered is to be removed from the lowering point after the emergency lowering. In this case, the load is decoupled by means of the coupling device and can be moved freely.

A firm connection with the abutment is particularly suitable, as far as the load or a load carrier after the emergency lowering should not be removed from the Absenkort. Examples of suitable load carriers are, for example, elevator baskets in high-rise buildings or other load baskets.

In a preferred embodiment, the emergency lowering device according to the invention additionally has a run-up. Under run-up in the context of the present invention, an additional device is understood here, by means of which the emergency lowering the rope can be rewound onto the coil. The emergency lowering is available after winding the rope by means of the run-up for a further emergency lowering available. Suitably, the run-up is carried out electrically or mechanically. In the electrical embodiment of the run-up, this can be designed as an electric motor. In the mechanical variant, this can be carried out in the simplest form as a hand crank. Upon actuation of the run-up, the inhibiting device is suitably decoupled. This can be done with known measures, such as a freewheel. The use of a run-up is particularly suitable in the embodiment in which the Notabsenkgerät is attached to a building, ship or the like and the abzusenkende load is attached to the free end of the rope. After uncoupling of the rope end of the load to be lowered, the rope end can be rewound by means of run-up in a simple manner again and is available at the starting point, ie at the elevated point from which the emergency lowering should take place again available.

The inhibiting device comprises a central circumferential axis on which at least one hub body is arranged. Furthermore, the inhibiting device comprises an outer body within which rotate the hub body or bodies. At least one braking device is arranged between the outer body and the hub body. Optionally, the rotational speed of the cable reel, or of the revolving axle on which the cable reel is arranged, is transmitted to the axle or hub body of the escapement device by means of a transmission or a transmission gear. This results in a higher rotational speed of the hub body relative to the rotational speed of the axis of the cable reel. The resulting advantages will be explained below.

In a further embodiment, the hub body with the associated components such as outer body and braking device are arranged on the axis of the cable coil. In the last-mentioned embodiment, the optional transmission can take place by means of a planetary gear.

The emergency lowering device in its basic form will be explained below with reference to Figure 1 below.

FIG. 1 shows the lowering device 1 in the embodiment in which the lowering device 1 is fixedly installed in a building (B) or the like, the load to be lowered being fastened to the free end of the cable 3. The lowered load 12 is shown symbolically as a weight.

The Notabsenkgerät 1 comprising the axis 5, on the center of the cable coil 2 is arranged. The cable reel 2 is non-positively and / or positively connected to the axis 5. The cable coil 2 may optionally with cable guide devices be provided known type to prevent entanglement of the rope during operation. From the cable spool 2, the free end of the rope 3 can be unwound. The free end of the cable 3 ends in a coupling device 4. The coupling device 4 includes all suitable coupling devices, such as a snap hook. By means of the coupling device 4, the cable end is attached with suitable measures.

In the illustrated embodiment, the cable reel 2 and the escapement 6 are arranged on the axles 5 and 5a. The transmission of power from the axle 5 to the axle 5a or the hub body 7 arranged on the axle 5a takes place by means of suitable power transmission means, such as link chains or toothed belts.

The hub body 7 are also non-positively and / or positively arranged on the revolving axis 5a. The hub bodies 7 are integral components of the inhibiting device 6, which furthermore have a brake system (not shown) as well as an outer body 8. In rescue operation, the cable is unwound from the cable reel 2, wherein the cable reel 2 with the axis 5 and in cooperation with the force transmission means the hub bodies 7 are set in rotation. The rotation is slowed down by means of the brake systems in the inhibiting device 6, wherein the outer body 8 serves as an abutment. The outer body 8 is prevented by suitable measures at the entrainment, for example by attachment to the housing of Notabsenkgerätes. 1

The illustrated embodiment also has a run-up 48. As stated, the run-up 48 serves to rewind the cable 3 to the cable reel 2 after the emergency lowering. In the illustrated embodiment, the run-up is designed as a hand crank 49, wherein the hand crank is arranged on a separate axis 5b in the illustrated embodiment. When turning the hand crank 49, the rotation is transmitted by suitable means, such as chains or timing belt on the axis 5 and the cable 3 wound up. It is essential alone that the inhibiting device 6 in the opposite direction, namely for winding, is separated from the axis 5 of the cable coil in their force. This can be done for example by means of a freewheel 50. In the embodiment shown in Figure 12, it is also possible to combine the axles 5 and 5a, after which both the restraining device and the cable reel are arranged on the axle 5. In such an embodiment, the skilled person by means suitable means such as a freewheeling readily meet the previously given provisos.

FIG. 2 shows an embodiment of the emergency lowering device according to FIG. 1, wherein the load to be lowered is fastened to the emergency lowering device. The rope end of the rope 3 is attached to a suitable anchor point above the location from which the lowering is to take place. In this embodiment, the Notabsenkgerät is lowered simultaneously with the lowered load. In the illustrated embodiment, the load 12 to be lowered is fastened to the housing of the emergency lowering device 1 by means of a holding device 9 and carrying lines 10, the carrying lines 10 being brought together in a load receptacle 11 which receives the load 12 to be lowered. In the embodiment of Figure 2, the run-up 48 is designed as an electrically powered run-up. The electrical power can be done by means of battery or electrical cable (not shown).

Preferred braking systems for controlling the lowering speed will be explained below. A preferred brake system is a hydraulic brake system. Submodes of the hydraulic brake system will be explained below with reference to FIGS. 3 to 5.

FIG. 3 shows a cross section through the hydraulic brake system in its simplest embodiment. Figure 2 shows the axis 5, on which a roller body 13 is arranged. The roller body 13 acts as a hub body in this embodiment. In known manner, at least two, preferably four, recesses are introduced into the roller body 13, for receiving the wing blades 14. Embodiments with three, five, six, seven, eight or more recesses for receiving wing blades 14 are also possible.

FIG. 3 shows an embodiment with four wing louvers. The wing blades 14 are pressed under the action of the pressure springs 15 on the inside of the cylindrical outer body 8. The axis 5 is eccentric and arranged in position fixed to the center of the cylindrical outer body 8. This will be in known manner, the asymmetric annular gap 16 is formed. The annular gap 16 is divided into four segments (17 a, b, c, d) according to FIG. 2 by means of wing louvers 14. The annular gap 16 is further filled with a liquid, preferably hydraulic oil. The wing blades 14 have control bores in this embodiment. The control bores extend transversely through the vane fins and are arranged so that they are not obscured by the roller body 13 when the vane fins 14 are dipped into the recesses. Through the control bores, a controlled flow of the liquid, preferably of the hydraulic oil, in the annular gap 16 between the segments 17 is possible.

When lowering operation, the axis 5 is rotated by unwinding of the cable 3, which entrains the roller body 13 thereon. Referring to Figure 3, the function will be further explained for clockwise rotation. An opposite direction of rotation is also possible.

Due to the eccentric arrangement of the roller body 13 within the outer body 8 in the clockwise rotation, the volume of the segment 17 a, formed by the roller body 5, outer body 8 and blade louvers 14, continuously reduced. The liquid in the segment 17 a is thus pressurized and thus provides a rotational resistance, which leads to the inhibition of Notabsenkeinrichtung 1. The liquid passes through the control bores within the wing blades 14 in the segment 17 b. The flow rate and thus the inhibition is adjusted by means of size and / or number of control bores. At the same time, the opposite process takes place, for example, in the segment 17c, the volume of which increases as it rotates. The inhibition is effected here by the resulting negative pressure in the segment 17 c, which takes place by flow of the liquid from the segment 17 b through the control bores of the arranged between the segments 17 b and 17 c wing blade 14. For the purposes of the present description, for example, the segment 17 a after a 90 ° rotation to segment 17 d. It will be understood by those skilled in the art that the illustration shown is a temporal snapshot of a dynamic rotating system. In summary, in the illustrated segments 17 a and 17 b due to the reduction in volume and in the segments 17 c and 17 d due to the increase in volume creates an inhibitory effect. FIG. 4 shows a development of the inhibiting device according to FIG. 3. In this case, of the compressing segments 17 a and b, a ring line is arranged relative to the expanding segments 17 c and d. In the ring line 18, a further control valve 19 is arranged. In this embodiment, the ring line 18 acts in the sense of a bypass. Conveniently, in this embodiment, the control bores in the vane fins 14 are designed so that the emergency lowering device, with the largest load to be assumed, for example a very heavy person, causes such an inhibition that a suitable sinking speed is achieved. In other words, in the embodiment according to FIG. 4, the control bores are designed such that they have a lower permeability to the liquid and thus an increased inhibition compared with the embodiment according to FIG. 3.

In the embodiment shown in Figure 4, the liquid is partially pressed during the compression in the segments 17 a and / or 17 b in the ring line 18, which opens on the opposite side of the outer body 8 in the segments 17 c and / or 17 d, in which the volume is increased again during operation. The flow of the liquid through the loop 18 is adjusted by the control valve 19. By increasing or decreasing the passage in the control valve 19, the flow resistance and thus the inhibition of the brake system is adjusted in this way.

It is based on the knowledge that in this embodiment, only a portion of the liquid must pass through the control bore, while another part of the liquid is discharged through the loop 18.

This embodiment has the advantage that the discharge speed can be manually controlled by the operator. Furthermore, this embodiment allows lighter persons with the same rescue device can be roped at a sufficiently high speed to leave the danger area quickly. FIG. 5 shows a development of the embodiment according to FIG. 4, wherein a further branch line 20 branches off from the ring line 18 and ends in a control module 21. The control module 21 acts on the control valve 19.

The illustrated embodiment shows a Notabsenkgerät with automatically regulating Abseilgeschwindigkeit at different loads, or to be rescued persons with very different weights.

When using the Notabsenkgerätes with a large load or a heavy person, the rotational speed of the roller body is increased with the associated facilities under its gravitational effect. This results in an increase of the hydraulic pressure in the line system 18 and 20 and the control module 21. The increasing hydraulic pressure is registered by the control module 21 and the control valve 19 readjusted.

In the load-free state, the control module 21 holds the control valve 19 in the open or largely open position. If the rescue device is now loaded with a large load, the pressure within the system rises and the control valve 19 is closed in proportion to the increase in pressure, until eventually complete closure. Thus, the escapement runs only on the control bores of the vane fins 14. Advantageously, the Lastabsinkgeschwindigkeit is kept largely constant within large weight tolerances of the load or abzuseilenden person.

A suitable control module 21 may comprise a pressure-resistant body having a control diaphragm 22 inside, the control diaphragm being loaded on one side by the fluid. On the opposite side of the control diaphragm is the spring 23, which acts against the hydrostatic pressure and holds the control valve 19 in the open position by means of a coupling member in the unloaded case. When pressurizing the liquid in the stub 20, the control diaphragm 22 acts against the spring 23 and by means of the coupling member on the control valve 19. The control effect by the strength of the spring 23 is arbitrarily adjustable. Another suitable embodiment for a brake system is explained below in FIGS. 6 and 7. In the embodiment shown is a mechanical braking device according to the principle of centrifugally controlled brake. FIG. 6 shows a cross section through the braking device perpendicular to the axis of rotation. The braking device in the illustrated embodiment comprises two brake shoes 24. In other embodiments, not shown, the use of only one or more than two brake shoes is possible.

The brake shoes 24 are configured semicircular in a conventional manner, in each case corresponding to the cylindrical inner side of the outer body 8. Furthermore, the brake shoes 24 are attached to one leg by means of axes 25 on the bottom plate 26 swung out. The bottom plate 26 acts as a hub body 7 in this embodiment. The bottom plate 26 is rotated by the axis 5a. Conveniently, a transmission gear can be arranged between the axis 5a and the bottom plate 26. The output of the transmission gear acts in this case as an axis 5a. The transmission can e.g. be designed as a planetary gear. By this artifice, the rotational speed of the bottom plate 26 is significantly increased with the associated modules relative to the rotational speed of the axis 5. At the same time, the torque is lowered by the aforementioned measure.

In rescue operation, the force of gravity of the attached load, or the person to be rescued acts on the cable spool 2 and thus on the axis 5, which is thus set in rotation. The axis 5 forms the input for an optional ratio, in which an increase in speed takes place with simultaneous torque reduction. The output of the translation acts on the axis 5a and thus on the bottom plate 26, which is thus set in rotation. By the rotation act on the brake shoes 24 in a conventional manner centrifugal forces that cause an erection of the brake shoes 24 against the inner wall of the outer body 8. The friction of the brake shoes 24 on the inside of the outer body 8 leads to the desired inhibition. The provision of the brake shoes 24 after termination of the Abseilbetriebes done by return springs 27 (Figure 7).

The illustrated embodiment has the advantage of self-control of the inhibition effect and thus the abseiling speed. For heavy loads, or heavy persons, it initially comes in abseiling to an increased speed, which increases the speed of the bottom plate 26 with the associated components. This in turn has an increase in the centrifugal force acting on the brake shoes 24 result, which in turn leads to increased contact pressure of the brake shoes 24 on the inside of the outer body 8 and thus in turn to an increased braking effect.

FIG. 7 shows a development of the embodiment according to FIG. 6, wherein the illustrated braking device has further devices for manual action on the braking device. This embodiment allows user intervention to reduce sink rate, to halt abseiling operation. This embodiment is particularly suitable for rescue workers, for example, as far as the rescuers abseil in a high-rise fire from a higher floor to accommodate a person to be sheltered in a floor below. In this case, the abseiling process can be interrupted at the level of the person to be rescued, the person is taken up and the abseiling process continues to the ground.

In the embodiment according to FIG. 7, the brake shoes 24 each have an arcuate projection 28 in the middle. The projection 28 is formed so that the projections of the sum of all the brake shoes 24 together form an inner cone. Furthermore, the embodiment has a cone 29 which is arranged free-running on the displaceable cone axis 30. Freewheeling in the sense of the present invention means that the cone can rotate about the cone axis 30. The cone axis 30 with the cone 28 thereon is arranged so that it can be pressed by means of the squeezing device 31 into the inner cone, formed by the arcuate projections 28. Furthermore, this embodiment has a handset 32 for actuating the squeezing device 31. Suitably, the squeezing device 31 can be operated hydraulically or mechanically by means of the handset 32.

To slow down the abseiling or to bring the abseiling to a halt, the operator can operate the handset 32, which is moved by the action of the squeezing 31 of the cone 29 in the inner cone formed by the arcuate projections 28. At contact of Cone 29 with the inner cone formed by the curved projections 28, the cone 29 is taken from the rotating brake shoes 24. The cone 29 then rotates freely on the cone axis 30. Upon further expressions of the cone 29 is further pressed into the inner cone formed by the arcuate projections 28, whereby a spreading action is exerted on the brake shoes 24. The spreading effect and the associated contact pressure of the brake shoes on the inside of the outer body 8 can be arbitrarily controlled by the scope of the squeezing means of the squeezing device 31 via the handset 32. The forces thus applied to the brake shoes 24 act in addition to the braking forces generated by the centrifugal force.

Upon release of the handset, the cone 29 is retracted by a suitable return device, here in the form of the return spring 33. When retracting the cone 29, the spreading effect is reduced, whereby the brake shoes are released again. The braking effect is then effected alone again by the centrifugal forces in the aforementioned sense.

Another suitable brake system for controlling the abseiling speed is a pneumatic brake system and will be explained below with reference to FIGS. 8 to 11.

Figure 8 shows the pneumatic brake system in its simplest embodiment. The pneumatic braking device comprises cylinders 33 arranged on the outer body 8. In the illustrated embodiment, the pneumatic braking device comprises eight cylinders. The number of cylinders with the associated modules can be varied easily. So it is possible to use braking devices with two, three, four, five, six, seven or more cylinders. Furthermore, an eccentric 37 is arranged on the revolving axis 5a. In this embodiment, the eccentric acts as a hub body 7. The eccentric 37 will be explained in more detail below. The eccentric 37 has a circumferential groove 40. In the circulation groove 40 can run roller bearings 39, which are arranged at the lower end of a piston rod 35. At the opposite end of the piston rod 35 is the piston 34, arranged in the cylinder 33. A lateral buckling or warping of the piston rod 35 is prevented by the piston rod guide 36. FIG. 9 shows the cylinder 33 in enlarged detail. The cylinder 33 is designed as a substantially closed cylinder, in which the piston 34 can oscillate. To the piston 34, the piston rod 35 connects, which is sealed relative to the cylinder 33. In the representation below the cylinder 33, the piston rod guide 36 is arranged, which ensures a vertical guidance of the piston rod. At the other end of the piston rod, the roller bearing 39 connects. Furthermore, the cylinder 33 control bores or control nozzles 41, respectively disposed at the upper and lower ends of the cylinder.

In Abseilbetrieb the axis 5 is rotated according to the previously made representations of other embodiments, on which the eccentric 37 is arranged. By means of the eccentric 37, the pistons 34 are set in an oscillating motion via the piston rods 35. When retracting the piston 34 is a compression of the above the piston 34 in the cylinder 33 located gas, preferably air, instead. The compressed gas is controlled by the upper control bore 41 controlled against a resistance, whereby the movement of the piston 34 is inhibited. At the same time a negative pressure in the corresponding space of the cylinder 33 is formed on the opposite side of the piston 34 by the movement thereof. The compensation takes place in accordance with the lower control bore 41. The movement of the piston 34 thus takes place simultaneously against an overpressure in the direction of movement and a negative pressure on the side thereof. In other words, the system is double inhibited. The setting of the inhibition can be done easily by selecting the control bores or suitable control nozzles.

Furthermore, it is possible for the braking device to precede a transmission gear, as described above. The use of a transmission gear has the advantage that the rotational speed of the braking device is increased, while reducing the torque. The aforementioned measure leads to an improvement in the controllability and the effect of the braking devices.

By using a plurality of the aforementioned piston / cylinder units in asymmetric working position, the suspension or reduction of the inhibition in the uppermost or lowermost position of the piston 34 in its travel in the cylinder 33 compensated. This artifice provides continuous and even inhibition over the entire abseiling period.

Figure 10 shows a suitable embodiment of the eccentric 37. The eccentric 37 consists according to the illustrated embodiments of two mirror-image-shaped half-parts. The half parts each have eccentric axle receptacles 42 for receiving the axle 5a. Circumferentially, the half parts continue to have a circumferential rim 43, forming the circulation groove 40. The circulation groove 40 takes in the installed state, the roller bearings 39 on. The roller bearings 39 can rotate freely in the circulation groove 40 during rotation of the eccentric 37.

FIG. 11 shows a development of the pneumatic braking device according to FIG. 8 with a standstill brake. The standstill brake comprises opposed pistons 45 which are arranged in the cylinder 33. The arrangement of the counter-piston 45 takes place on the side of the axis 5a opposite to the piston 34. Notwithstanding the embodiment of Figure 8, the cylinder is provided on the outside with an opening which has no control effect. The control bore is in this embodiment within the counter-piston 45. Optionally, the counter-piston 45 may be provided on the piston 34 side facing with a brake buffer 46. A suitable brake buffer consists for example of an elastomeric block. The counter-piston 45 is attached to the adjusting ring 44 by suitable means, such as a piston rod. By means of the adjusting ring 44, the counter-piston 45 can be adjusted in its position in the cylinder 33. A suitable measure is the use of a positive guide 47.

In normal Abseilbetrieb the respective counter-piston 45 in its initial position, that is arranged at the outer end of the cylinder 33. The abseiling runs in this position according to the embodiment of Figure 8. In order to bring the Abseilbetrieb to a standstill, or the counter-piston 45 are retracted under the action of the adjusting ring 44 in the cylinder 33. This briefly increases the compression in the intermediate space between piston 34 and counter-piston 45, which leads to increased inhibition and thus braking effect and a slowed abseiling. Upon further retraction of the opposed piston 45 in the cylinder 33 occurs at least one of the opposed piston used in the travel of the associated piston 34, whereby the Piston 34 to the counter-piston 45, possibly under the action of the brake buffer 46, abuts and thus brought to a standstill. A further rotation of the axis 5a is thus prevented and the abseiling interrupted.

To continue the abseiling process, the counter-piston 45 is returned to its initial position in the respective cylinder 33, with the return of the adjusting ring 44, with which the piston 34 again has the travel path available. Under the effect of gravity of the person to be rescued, or the suspended load of abseiling is resumed immediately.

The illustrated embodiment of Figure 11 has the advantage that the deceleration can be carried out to a standstill by the operator without further measures, namely by adjusting the adjusting ring, after which the resulting increased damping effect leads to a gentle braking without further action by the operator.

LIST OF REFERENCE NUMBERS

1. Emergency lowering device

2. rope coil

3. rope

4. Coupling device

5. 5a, 5b axis

6. Braking device

7. hub body 8. outer body

9. holding device 10. carrying lines

11. Person recording

12. Last

13. Roller body 14. Vane fins 15. Pressure springs 16. Annular gap 17.Segements 18. Ring line

19. Control valve 20. Stub line 21. Control module

22nd control membrane

23. Spring

24. Brake shoes 25th axis

26. Base plate

27. Return spring 28. arcuate approach

29th cone

30. cone axis

31. Expressing device

32. Handset 33.Cylinder

34. Piston

35. Piston rod

36. Piston rod guide 37. eccentric 38. rollers

39. Roller bearing 40. Circumferential groove

41. Control bore / control nozzle 42. Axle holder 43. Wreath 44. Adjusting ring

45. Opposite piston

46. Brake buffer

47. Forced operation 48. Run-up 49. Winch

50th freewheel

Claims

Our sign: HOKA 9 Applicant: by Gencsy 19.12.2005Ansprüche

1. A device for emergency lowering of loads and / or persons, characterized in that the Notabsenkgerät (1) comprises a circumferential axis (5) with a non-positively coupled thereto cable coil (2) wherein the device comprises at least one hub body (7), wherein the Hub body (7) by an outer body (8) is rotatably enclosed and between the hub body (7) and the outer body (8) a braking device (6) is arranged.

2. Device according to the preceding claim, characterized in that the cable coil (2) by means of a transmission or a transmission gear is frictionally coupled to a rotating axis (5 a).

3. Device according to claim 1, characterized in that the hub body (7), outer body (8) and braking device (6) on the axis (5) of the cable coil (2) are arranged.

4. Apparatus according to claim 3, characterized in that, the cable reel (2) via a planetary gear is positively connected to the axis (5).

5. Device according to one of the preceding claims, characterized in that the braking device is a hydraulic braking device.

6. The device according to claim 5, characterized in that the hub body (7) is designed as a roller body (13), wherein the roller body has at least two vane lamellae (14) arranged in the roller body (13) arranged recesses, wherein the axis (5). is arranged eccentrically in the interior of the outer body (8), forming the asymmetrical gap (16), wherein the gap (16) is filled with a liquid and further the wing blades (14) have control openings.

7. Device according to claims 5 or 6, characterized in that the liquid is hydraulic fluid.

8. Device according to one of claims 5 to 7, characterized in that the device further comprises a ring line (18) connecting the compressing portion of an annular gap (16) with the expanding portion of the annular gap, wherein further in the ring line (18) a Control valve (19) is arranged.

9. The device according to claim 8, characterized in that the ring line (18) further comprises a stub line (2) comprising a control module (21), wherein the control module (21) acting on the regulating valve (19) acts.

10. Device according to one of claims 1 to 4, characterized in that the braking device (6) is a mechanical braking device.

11. The device according to claim 10, characterized in that the hub body 7 is formed as a bottom plate (26), wherein on the bottom plate (26) at least one brake shoe (24) is arranged, which on a leg by means of axis (25) can be swung.

12. The device according to claim 11, characterized in that at least two brake shoes (24) are provided, wherein the brake shoes (24) further each having an arcuate projection (28), forming an inner cone, wherein the braking device further comprises a cone (29) ,

13. The apparatus according to claim 12, characterized in that the cone (29) by means of squeezing device (31) is actuated.

14. Device according to one of claims 1 to 4, characterized in that the braking device (6) is a pneumatic braking device.

15. The device according to claim (14), characterized in that the hub body (7) as an eccentric (37) is formed, connected to at least one piston (34) which can oscillate in the associated cylinder (33), wherein the cylinder ( 33) has at least one lower control bore (41).

16. The apparatus of claim 15 or 16, characterized in that the eccentric (37) is formed from two Hatbteilen, each comprising a circumferential rim (43) forming the circumferential groove (40).

17. Device according to claims 15 to 17, characterized in that the braking device has at least two piston / cylinder units in asymmetric working position.

18. Device according to one of claims 14, 15, 17 or 18, characterized in that in the cylinder (33) an opposed piston (45) is arranged, wherein the counter-piston (45) further comprises a control bore (41).

19. The apparatus according to claim 19, characterized in that the counter-piston (45) on the piston (34) facing side with a brake buffer (46) is provided.

20. The apparatus of claim 19 or 20, characterized in that the counter-piston (45) by means of a adjusting ring (44) in its position in the cylinder (33) is adjusted.

21. Device according to one of the preceding claims, characterized in that it comprises a coupling device (4) at the free end (3) of the rope.

22. Device according to one of the preceding claims, characterized in that, said means (51) for local, fixed mounting of the device to a building B has.

23. Device according to one of the preceding claims, characterized in that it has a run-up (48) for winding the rope.

24. The device according to claim 23, characterized in that the run-up (48) by means of a hand crank (49) is operated.

25. The apparatus according to claim 23, characterized in that the run-up is electrically, pneumatically, hydraulically or mechanically driven.

26. Device according to one of claims 23 to 25, characterized in that the run-up (48) via a freewheel (50) is non-positively coupled to the cable coil (2).