SI25029A - Rope braking device - Google Patents

Abstract

The invention relates to a rope braking device in which, by varying the design parameters, it can be achieved that it acts as a guard, a brake, a rope drop rotor or a positioning device. The rope braking device (1) comprises a substantially flat base element (2) with the upper portion (2a) with a first hole (3) for receiving both ends of the rope (6) and with the lower section (2b), an axis which, with the upper portion 2a) forms an alpha which is from 60 to 110 degrees, a rotatable element (5) mounted on the axis, and a pressure element (7) attached to the panel element (5) such that the axis of the elemental element (5 ) and the axis of the pressure element (7) are enclosed as beta, which is 60 to 90 degrees. The end sections along the longitudinal side of the upper section (2a) are mutually enclosed as omega, which is 90 to 180 degrees. The device is structurally simple, safe and reliable, it acts on both sides, it enables optimum operation by using a wide range of different rope thicknesses.

Description

ROPE BRAKE DEVICE

Technical area

The invention relates to a plurality of rope braking devices having a common inventive concept, whereby various functional characteristics are achieved by changes in the design so that the device can be used as a fall arrester, as a brake, as a fall shock absorber or as a positioning device, namely climbing, alpinism, caving, rescue, altitude protection, industrial applications, transportation and nautical.

The state of the art

Various designs of rope braking devices are known in the art. The three basic functions that rope braking devices must fulfill are the following: they must allow the rope to move freely through the device when the rope is not in the loaded position; they must brake the rope when it is loaded; and must allow for a controlled release of the loaded rope through the device. These functions are basically excluded, so it is difficult to ensure that all three functions are fulfilled on one device. Depending on the intended use of the device and the requirements of the standard, one or the other function is given greater importance. The basic four types of rope braking devices are: a braking device, a safety device, a positioning device and a shock absorber.

For the device to hold the rope, it is necessary to create conditions of friction between the rope and the parts of the device. Two types of rope wiring are common. In the first case, the rope passes through the device without kinks, which in an unloaded state allows unimpeded movement of the rope through the device, and in the second with kinks, which impedes the free movement of the rope through the device. In the case of no twisting of the rope, a strong surface pressure of the brake part of the device against the rope is required, in which case the braking force is calculated by the formula of the surface pressure with the corresponding coefficient of friction between the materials. The rope is thus point-loaded and therefore more exposed to damage and wear than in the case of a rigid rope where the friction force is distributed over a larger surface. In this case, the braking force is linearly proportional to the force of the surface pressure on the rope. The brake force defines the coefficient of friction, the radius of curvature of the rope, and the angle of contact of the surface contact between the rope and the sliding surface of the roller or parts of the device. The braking force increases exponentially as the rope angle and the friction coefficient increase.

The characteristics of the rope vary depending on the manufacturer and the type of rope, the thickness of the rope, the wear, age and absorption of the rope by oil, water, mud, sand. All of these variables affect the performance of the device. The operation of the device is also affected by the loading force and the loading speed of the rope. These variables affect the performance of the device in different circumstances, thereby reducing the safe operation of the device. However, reliability and safety are key, so there is a need for a device that ensures stable operation in all conditions.

There are two ways of stopping the movement of a loaded rope, either "dynamic" with a slip or "static" without slipping the rope through the device. Dynamic slip stop is used e.g. for fall shock absorbers. In the case of a static motion stop, the force is impulse. In this case, the energy is absorbed by elongation of the rope or by friction in the rope. In dynamic stopping motion, the loading force and the stopping distance are interdependent, and the braking force at which the slip occurs varies depending on the thickness, the hardness of the rope, and the execution of the braking mechanism of the device. In this case, the device absorbs some of the energy by friction between the rope and the parts of the device, the rest of the energy is absorbed by elongation and friction in the rope.

For static stopping of the movement of the rope through the device, the mechanism with the eccentrically clamped oscillating part of the mechanism is most commonly used, which acts self-tightening when pressed against the rope. Such a mechanism is disclosed in document DE2439678A1. The disadvantage of this solution is the high system loading forces that can lead to damage to the rope or parts of the system and a higher force on the lever acting on the eccentric to relieve the system. To the extent that the movement of the eccentric is restricted and the rope is slipped, there is a problem of adjusting to different rope thicknesses, which in turn limits the usefulness and safety of the device. In addition, the eccentric pressure forces on the rope depend on the eccentric position, which depends on the rope thickness.

In order to dynamically stop the movement of a rope by sliding through the device, the simple mechanism through which the rope is wrapped is most often used. A description of such a mechanism is contained in document FR2631325A1, which serves as a retainer or brake for rope-lowering.

In the field of height protection, for sports and industrial applications, two types of fall shock absorbers are commonly used. One type usually uses a sewn multiple folded strip where the seams begin to tear at the load to absorb the fall energy. This type of drop damper is most used in industrial applications, a typical example of which is found in document US3444957. The disadvantage of this damper is that it is disposable. The second type of fall damper is divided into two subspecies. The first sub-type uses a non-movable hole-shaped plate through which a rope is dimensioned, which is dimensioned to the diameter of the holes in the plate. The advantage is the ease of implementation and the disadvantage is that the braking conditions change with changes in the rope as it becomes less flexible and harder over time, resulting in an increased braking force that makes the device unsafe to use. Such a device is described in document DE3345290A1. The second sub-category of the shock absorber uses a mechanism that allows the rope to slip under a certain force and is usually used as a buffer and a shock absorber at the same time. These are self-locking guards for heavy loads as described in EPI 123718A1. The advantage of this self-locking damper or guard is that it can be reused several times and has the possibility of controlled load lowering and that it can hold large loads due to the large circumference of the rope around the moving part of the braking mechanism. The disadvantages, however, are the inflexible brake force, the very limited use of different thicknesses of rope, the difficult movement of the rope through the device when it is not loaded, the size, weight and consequently the high cost.

• · · · ·

The safety devices are separated into self-tightening guards and those in which the fall of the climber is stopped by manual restraint of the rope at the entrance side. Self-locking guards typically use an eccentric brake mechanism, as disclosed in document US5076400A. These self-tightening devices forcefully stop the drop, which is uncomfortable for the climber and can also be dangerous for the guard, as the force of the rope lifts him off the ground and can hit the rock. Large forces are also problematic for anchorages that rock climbers make while climbing. The advantage of self-tightening devices is that the rope does not slide through the device when the rope is not held by hand, thus preventing the climber from falling freely and hitting the obstacle. Because these devices provide higher security, they are desirable, although more expensive, larger, more difficult, and use a mechanism that does not work reliably in certain circumstances, which are undesirable characteristics of the device. Self-tightening device allowing one to slip the rope at lower forces, discloses document US2003196853A1. Despite automatic braking, these devices do not yet provide full safety, as the mechanism may not detect a fall and stop the rope from sliding. Therefore, the climber should never drop the rope during the guard. An example of a device that solves this problem with a centrifugal clutch that detects a fall relative to the speed of rope movement through the device is described in US2014262611Al.

Other devices where the fall of a climber is stopped by manual rope restraint provide dynamic protection or soft fall arrest, which is enabled by manually controlled sliding of the rope through the device. Such a device is disclosed in US D593844. Because these devices have relatively low braking power, it is difficult to hold down in the event of a major fall. Because the forces of such a fall can be higher than can be held by hand, there can be fatal consequences of a climber falling and damaging the arm of the person protecting him or her while holding the rope. Improvements to increase the braking power of the device are made with an enlarged V groove that operates partly smog-free, as disclosed in US2011284323A1, but the problem with the danger of the rope being dropped still exists. In addition, the device is quite aggressive to the rope, which is reflected in the wear and tear of the rope, especially in the case of descent.

Typically, devices that stop the rope dynamically allow the rope to slide freely through the device when the rope is unloaded, while self-tightening guards impede this movement of the rope significantly and trigger the braking mechanism faster and more often, especially when the rope is pulled quickly, which bothers the climber. as it keeps him from climbing. To remedy this problem, various techniques of manual restraining of the braking mechanism are used, but this increases the possibility that the device does not detect a fall and the guard does not instinctively release the restraint of the braking mechanism during the fall, which reduces the safety of the safety device. Both types of devices have advantages and disadvantages, which is the advantage of one being the disadvantage of the other device and vice versa, so there is a need for a device that combines the good features of both types of devices. An attempt to combine dynamic and static security on a single device is disclosed in document US2014174850.

The basic function of the brake is the controlled descent. Self-locking brakes usually use an eccentric brake mechanism, so the rope slides through the device only at high forces, depending on the thickness of the rope, and ranges from 4 kN to 9 kN. An example is illustrated in US5054577A.

Positioning devices are used to position the worker at height, e.g. on an electric pole or roof when the rope system adjusts to a certain distance which restricts movement and thus prevents it from falling. An example of such a device is disclosed in US8464832B1.

A technical problem

The technical problem is how to design a rope brake device that will be structurally simple, small in size, light and affordable to manufacture. The goal is to design a multitude of rope brakes with a single structural design that, by modifying certain design parameters, meet the requirements of the standards for guards, brakes, rope dampers and positional devices. Furthermore, the rope braking device should allow for two-sided operation, operation with a large range of thicknesses and rigidity, a smooth sliding of the rope through the device when the rope is not loaded, and automatic activation of the braking mechanism under pulse load or. with increased speed of sliding rope through the device. In addition, the device should allow controlled relief.

The solution to a technical problem

A technical problem is solved with a rope brake device comprising:

- a substantially flat base element further comprising an upper portion of the base element having a first hole at the upper portion for receiving both ends of the rope and a lower portion of the base element,

- an axis which is fixedly connected to the lower part of the upper section of the base element by forming an angle a with the upper section of the base element in the longitudinal section;

- a twist element which is pivotally, preferably centrally positioned on the axis and around which a rope is routed, and

- a pressure member, preferably cylindrical, which is fixedly connected to the circumferential part of the suction element by projecting upwards therefrom, with the axis of the suction element and the axis of the pressure element curving as β.

The rope brake device comprises a second hole for receiving the carriage, which is optionally disposed on the lower part of the lower section of the base member or on a support arranged in the axis of said axis.

In the working position of the rope brake device, the rope runs from the upper side through the first hole, around the twist element and again through the first hole from the bottom. The direction of rope introduction to the device is irrelevant as the device operates on both sides. In the unladen state of the rope, it slides freely through the rope brake device. When one end of the rope is subjected to a force impulse or the speed of sliding of the rope is greatly increased, it rotates due to the friction between the rope and the twisting element, the compression element squeezes against the inner surface of the upper section of the base element and inhibits the sliding of the rope through the rope brake device.

The rope brake device may further comprise a ball, a spring and a locking element which are arranged in a third through hole formed in the longitudinal direction of the pressure member. The ball, loaded with the help of a prestressed spring, in the unloaded state of the rope brake device engages a fourth hole formed in the element on which the twisted element is located and prevents the rope brake device from being actuated too quickly, ie. when the rope slides freely through the device. As the speed of the rope through the rope brake device increases, the friction between the rope and the twist element pushes the ball against the force of the spring from its locked position and the twist element can rotate around the axis.

The braking force depends on the circumference angle γ of the rope. The larger the angle γ, the greater the braking force. The circumference of the rope determines the ratio of the diameter d of the twist element to the width a of the first hole. Other mechanisms for increasing the braking force will be explained below.

The end sections along the longitudinal side of the base element enclose each other as ω.

Different configurations of the rope brake device are possible. The parameters are selected depending on which function of the device we want to prioritize, ie. depending on the purpose of the device.

One of the configurations of the design parameters of a rope brake device is when the angles a and β are equal and are essentially 90 °. The angle ω is essentially 180 °. The push element moves parallel to the inner surface of the base element. Depending on the distance b • · of the pressure element from the inner surface of the base element and on the thickness of the rope, in a loaded state, the pressure element presses the rope against the inner surface of the base element or the edge of the first hole. The offset b therefore determines the braking force, which depends on the thickness of the rope. Such a design of the rope brake device is particularly suitable for use as a brake, positioner or fall shock absorber.

Another configuration of the design parameters of a rope brake device is when the angles a and β are equal and greater than 60 ° and less than 90 °. The angle ω is twice the angle β. The inner face of the base element is an approximation of the sheath of the truncated cone, whose center line is aligned with the axis of the twist element so that the pressing element moves parallel to the inner face of the base element. Depending on the distance b of the pressure element from the inner surface of the base element and from the thickness of the rope, the pressed element in a loaded state pushes the rope against the inner surface of the base element or the edge of the first hole. In this case, the offset b also determines the brake force, which depends on the thickness of the rope. Such a design of the rope brake device is similar in functionality to the first embodiment, except that it is more sophisticated in design and more ergonomically suitable for handling. It is especially suitable for use as a positioning device, brake or fall damper.

The third configuration of the design parameters of the rope brake device is when the angle a is greater than 90 °, preferably between 100 ° and 110 °, and the angle β is 60 ° to 90 °, preferably 90 °. The angle ω is 90 ° to 180 °, preferably between 110 ° and 130 °. Greater than a means greater braking force. In this case, the pressure element does not move parallel to the inner surface of the base element. A wedge-shaped space is formed between the pressure element and the inner face of the base element, in which a cord is to be wedged to be twisted. In this embodiment, the wedge space adapts to different rope thicknesses. The braking force is maintained independently of the thickness of the rope. Such design of the rope brake device is suitable for use especially as a guard. To the extent that the device is equipped with a deflection element, as described below, it is also suitable for use as a positioning device, brake or shock absorber.

To increase the braking force of the rope brake device, a twist element opposite to the pressure element may be provided with a first deflection element. The first deflecting element deflects a rope that runs around the twist element in a plane transverse to the axis of the twist element by a distance c from the inner surface of the base element. The braking force is further increased if the first deflection element is formed at an angle such that the angle δ between the axis of the twist element and the axis of the first deflection element is less than 90 °, preferably between 60 ° and 80 °.

Alternatively, the rope brake device may comprise a second deflection element integral with the base element, internally at the top of the lower section of the base member. The second deflection element causes the rope to distance c away from the inner face of the base element. Its function is similar to that of the first deflection element, except that the effect on increasing the braking force is less. The braking force is further increased if the second deflection element is angled so that the angle δ between the axis of the pivot element and the front face of the second deflection element is less than 90 °, preferably between 60 ° and 80 °.

The device further comprises a release lever which allows the rope brake device to be controlled reliably by hand in the event of lowering.

A groove may be formed at the upper end of the base element in the longitudinal direction of the base element. The groove serves to receive the free end of the rope. The rope is bent over the groove, which increases the braking force during the controlled lowering of the climber and thus improves braking control.

The advantage of the rope brake device according to the invention over the known devices is the simple construction with a small number of parts, its small dimensions and light weight and low production cost. Uniform design by varying certain parameters makes it possible to produce a device that complies with the requirements of the international standard for guards, brakes, rope dampers and positioners. A further advantage is the two-way operation of the rope brake device, which means that there can be no fatal error in routing the rope through the device. The advantage of the rope braking device over the known devices is also its great insensitivity to different thicknesses and hardnesses of the rope, as it enables the optimum performance of the device by using a wide range of different rope thicknesses. It enables smooth sliding of the rope through the device when the rope is not loaded, as well as automatic actuation of the braking mechanism under pulse load or. with increased speed of sliding rope through the device (eg above 1 m / s). An important advantage of the rope safety device according to the invention is that the brake is actuated in every situation, even if the free end of the rope is not held by hand.

Figure 1: Rope braking devices known in the art; a. self-locking guard, b. self-tightening eccentric brake, c. conical positioning device, d. eccentric positioning device, e. parking brake with rollers, f. fall damper with hole plate, g. parking brake (eight), h. tubular hand guard

Figure 2: Two ways of using a rope brake device according to the invention when in function of a guard

Figure 3: Rope brake device with a first deflection element with angles a and β of 90 ° and ω 180 °

Figure 4: Rope braking device with bracket and anti-accelerator mechanism

Figure 5; Rope braking device with bracket and mechanism to actuate too quickly the rope brake device in cross section

Figure 6: Rope braking device with support and first deflection element at angles a and β of 90 ° and ω 180 °

Figure 7: Rope braking device with support and other deflection element with angles a and β less than 90 ° and ω less than 180 ° • # ll - -: · ·. . . * '' * * ·

Figure 8: Rope braking device with bracket having a angle greater than 90 °, β 90 ° and ω less than 180 °

Figure 9: Illustration of the adaptation of the rope brake device to different thicknesses of the rope Figure 10: Rope in the rope brake device in the unloaded state Figure 11: Rope in the rope brake device in the loaded state

The invention will now be described in more detail below.

A technical problem is solved by a rope brake device 1 comprising:

- essentially a flat base element 2, further comprising the upper section 2a of the base element having a first hole 3 at the upper part for receiving both ends of the rope 6, and the lower section 2b of the base element,

- the axis 4, which is fixedly connected to the lower part of the upper section 2a of the basic element so as to form an angle a with the upper section 2a of the basic element;

- a twist element 5 which is pivotally, preferably centrally positioned on the axis 4, and around which a rope 6 runs, and

- a pressure element 7, preferably cylindrical, which is fixedly connected to the circumferential part of the rotary element 5 by projecting upwards therefrom, with the axis of the rotary element 5 and the axis of the pressure element 7 enclosing as β.

The twist element 5 is preferably cylindrical in shape, but may also be in the form of a truncated cone. It may also form a cross section in the cross section (eg square), but in this case the free sliding of the rope through the rope brake device in an unladen condition will be difficult. The twist element 5 may also be mounted on the axis 4 eccentrically, but in this case the braking force will be greater and the device will brake statically without slipping.

The rope brake device comprises a second hole 8 for receiving a carriage 17, which is optionally disposed on the lower part of the lower section of the base member or on a support arranged in the axis of said axis 4. The support may be provided in any known structural manner. It can be shaped axes, it can be mounted on said axis by means of pin 11 passing through that axis and the like. The twist element can be mounted on the axis with the intermediate arrangement of the sliding sleeve.

In the working position of the rope brake device 1, the rope 6 is guided from the top through the first hole 3, around the twist element 5 and again through the first hole 3 from the bottom.

The rope brake device 1 may further comprise a ball 12, a spring 13 and a locking element 14 which are disposed in a third through hole 15 formed in the longitudinal direction of the pressure member 7. The ball 12, which is loaded by means of a prestressed spring 13, in the unladen state The condition of the rope brake device 1 is harvested by the fourth hole 16, which is formed in the structural part on which the twist element 5 is positioned and prevents the rope brake device 1 from being actuated too quickly, ie. when the rope slides freely through the device. When the rope is slid freely through the rope brake device, the friction between the rope 6 and the twist element 5 is not great. When the speed of the rope through the rope brake device in the event of a fall, or the rope over the rope when the rope is released from the arm, increases, the friction between the rope and the twist element also increases and the latter pulls the ball 12 against the force of the spring 13 from its blocked position. The twist element 5 rotates about an axis. This mechanism is activated not only in the event of a shock load, but also in the case when the speed of the rope through the device increases gradually, which is important for the safe operation of the device.

The braking force depends on the circumference angle γ of the rope. The larger the angle γ, the greater the braking force. The clamping angle of the rope is determined by the ratio of the diameter d of the twist element 5 to the width a of the first hole 3. The clamping angle γ of the rope and thus the braking force, which increases exponentially as the clamping angle increases, is also affected by the thickness of the rope. A thinner rope means a smaller circumference angle γ.

The end sections along the longitudinal side of the upper section 2a of the base element enclose each other as ω.

The design parameters of the rope brake device are selected depending on which function of the device we want to give priority to, ie. depending on the purpose of the device.

One embodiment of a rope brake device 1 is when the angles a and β are equal and are substantially 90 °. The angle ω is essentially 180 °. The push element 7 moves parallel to the inner surface of the base element 2. Depending on the distance b of the pressure element 7 from the inner surface of the base element and the thickness of the rope, the pressure element 7 in a loaded state presses the rope 6 at the inner surface of the base element 2 or at the edge of the first hole. 3. The offset b therefore determines the braking force that depends on the thickness of the rope. Such a design of the rope brake device is particularly suitable for use as a brake, positioner or fall shock absorber.

Another embodiment of a rope brake device is when the angles a and β are the same and are between 60 ° and 90 °, preferably between 70 ° and 80 °. The angle ω is twice the angle β. The inner face of the base element is an approximation of the sheath of the truncated cone whose center line is aligned with the axis of the twist element 5 such that the pressure element 7 moves parallel to the inner surface of the base element 2. Depending on the offset b of the pressure element 7 from the inner surface of the base element 2 and from the thickness of the rope, the pressed element 7 in the laden state presses the rope 6 against the inner face of the base element or along the edge of the first hole 3. In this case, too, the deflection b determines the brake force, which depends on the thickness of the rope. Such a design of the rope brake device 1 is similar in functionality to the first embodiment, except that it is more sophisticated in design and more ergonomically suitable for handling. It is especially suitable for use as a positioning device, brake or fall damper.

The rope brake device 1 further comprises a limiter 21 of the twist movement of the twist element. It may be formed as a projecting element disposed on a base member against which a pressure element 7 rests in the loaded state of the rope brake device, preventing it from moving further. It is understood that the limiter may be formed in any structural way.

A third embodiment of a rope brake device 1 is when the angle a is greater than 90 °, preferably between 100 ° and 110 °, and the angle β is 60 ° to 90 °, preferably 90 °. The angle ω is 90 ° to 180 °, preferably between 110 ° and 130 °. Greater than a means greater braking force. In this case, the push element 7 does not move parallel to the inner surface of the base member. A wedge-shaped space is formed between the pressure element 7 and the inner surface of the base element 2 in the rotation of the twist element 5, in which a rope 6 is wedged, which is to be retracted. In this embodiment, the wedge space adapts to different rope thicknesses. The braking force is maintained independently of the thickness of the rope. Such an embodiment of the rope brake device 1 is suitable for use especially as a guard. Where a rope brake device is used as a safety device, the variants in which α = 110 °, β = 90 ° and ω = 130 ° or a - 110 °, β = 80 ° and ω = 120 ° shall prove to be the optimal combination of parameters. . In such a configuration of the rope brake device, dynamic braking is achieved by sliding the rope. Self-storage of the device is guaranteed, which is important for safety. The braking force can be affected by manually holding the rope, with the already small force of holding the rope by hand greatly increasing the braking force of the device. The thickness of the rope has no significant effect on the braking force. This applies to the thicknesses of the ropes normally used in fuses, ie. from 7,5 mm to 11 mm, and for brakes from 10 mm to 13 mm.

The rope brake device 1 further comprises a limiter of twist movement of the twist element. The formation may be a projecting element disposed on a base member against which a pressure element 7 rests in the loaded state of the rope brake device, thereby preventing it from moving further. It is understood that the limiter may be formed in any structural way.

In order to increase the braking force of the rope braking device, the twist element 5 on the opposite side of the pressure element may be provided with a first deflection element 9 which is disposed at an angle δ with respect to the axis of the twist element 5. The first deflection element 9 deflects the rope 6, which runs about the twist element 5, in a plane transverse to the axis of the twist element, by a distance c from the inner surface of the lower section 2b of the base element. The braking force is further increased if the first deflection element 9 is formed at an angle such that the angle δ between the axis of the pivot element 5 and the axis of the first deflection element 9 is less than 90 °, preferably between 60 ° and 80 °. A device equipped with a first deflection element 9 is suitable for use as a positioning device, brake or fall shock absorber.

Alternatively, the rope brake device may comprise a second deflector element 18 formed integral with the base element, on the inside at the upper portion of the lower section 2b of the base element. The second deflecting element 18 causes the rope to distance c away from the inner face of the lower section 2b of the base element. Its function is similar to that of the first deflection element 9 in that the deflection element determines the position of the rope in the rope brake device and thus the flow of rope through the device, but the braking force in this case is less. The braking force is further increased if the second deflection element is formed at an angle such that the angle δ between the axis of the twist element and the front face of the second deflection element is less than 90 °, preferably between 60 ° and 80 °.

The distance c affects the magnitude of the braking force, but also the flux of the rope through the rope locking device when in the unloaded state. Therefore, it is chosen depending on the desired characteristics of the rope brake device.

The apparatus further comprises a relief lever 25 which is connected to the rotary member 5 and enables controlled release of the rope brake device by hand in the event of lowering. The connection can be direct or through leverage.

A groove 19 may be formed at the upper end of the base member in the longitudinal direction of the base member 2. The groove 19 serves to receive the free end of the rope 6. The rope can be bent over the groove, thereby increasing the braking force during controlled lowering of the climber and thus improving braking control.

The apparatus may further comprise a housing which is not the subject of the present invention.

Claims (10)

A rope brake device (1) comprising: - a base element (2) with a first hole (3) for receiving both ends of the rope (6), - axis (4), which is fixedly connected to the base element (2), preferably a cylindrical push element (7) and - a second hole (8) for receiving the carabiner (17), characterized in that - the base element (2) is substantially planar and further comprises the upper portion (2a) of the base element, and the lower portion (2b) of the base element, wherein the first hole (3) for receiving the two ends of the rope is disposed at the upper portion of the upper portion ( 2a) the basic element, - the axis (4) is fixedly connected to the lower part of the upper section (2a) of the base element so as to form an angle a with the upper section (2a) of the base element, - that the rope brake device (1) further comprises a twist element (5) which is pivotally, preferably centrally located on the axis (4), and around which a rope (6) is routed, - the pressure element (7) is fixedly connected to the circumferential part of the rotary element (5) by projecting upwards thereof, with the axis of the rotary element (5) and the axis of the pressure element (7) wrapped as β, and - the end sections along the longitudinal side of the upper section (2a) of the base element enclose each other as ω. Cable rope braking device (1) according to Claim 1, characterized in that the angles a and β are substantially equal to 90 °, with the angle ω being substantially 180 °. Cable braking device (1) according to claim 1, characterized in that the angles a and β are equal to and greater than 60 ° and less than 90 °, preferably between 70 ° and 80 °, wherein the angle ω is twice the angle β. Cable braking device (1) according to claim 1, characterized in that the angle a is greater than 90 °, preferably between 100 ° and 110 °, the angle β is from 60 ° to 90 °, preferably 90 °, and the angle ω is from 90 ° to 180 °, preferably between 110 ° and 130 °. Cable braking device (1) according to any one of the preceding claims, characterized in that it further comprises a ball 12, a spring 13 and a locking element 14 which are arranged in a third through hole 15 formed in the longitudinal direction of the pressure element 7 , wherein the ball (12) loaded by means of a prestressed spring (13) engages a fourth hole 16 in the unladen condition of the rope brake device (1). Cable braking device (1) according to any one of the preceding claims, characterized in that it further comprises a first deflection element (9) disposed on the rotary element (5) opposite to the pressure element (7), and which is positioned at an angle δ with respect to the axis of the twist element (5). Cable braking device (1) according to any one of claims 1 to 5, characterized in that it further comprises a second deflection element (18) formed integrally with the base element (2) on the inside at the upper side part of the lower section (2b) of the base element, wherein the front face of the second deflection element (18) is disposed at an angle δ with respect to the axis of the twist element (5). Cable braking device (1) according to claim 6 or 7, characterized in that the angle δ is less than 90 °, preferably between 60 ° and 80 °. Cable braking device (1) according to any one of the preceding claims, characterized in that it further comprises a limiter (21) of the rotary movement of the rotary element (5). Cable braking device (1) according to any one of the preceding claims, characterized in that it further comprises a relief lever (25) which is connected to the rotary element (5).