F ield of Invention

The invention refers to a plurality of rope brake devices that all share a common concept of invention and in which changes in constructional properties entail various functional properties such that the device can be used as a belay device against a fall, as a rope descender, as a fall shock absorber or as a positioning device, all that in sports climbing, alpinism, speleology, rescue operations, height protection, industrial applications, transport and nautics.

Prior Art

A wide variety of rope brake devices are known from prior art. The fundamental three functions which must be met by all rope brake devices are as follows: they must allow a free rope movement through the device when the latter is in an unloaded state; they must brake a rope when it is loaded; and they must allow for a controlled descending of the loaded rope through the device. Basically, the mentioned functions exclude each other and it is therefore difficult to achieve all three functions to be fulfilled within a single device. Depending on the purpose, for which the device is used, and standard requirements, one or another function is attributed a more significant importance. T he basic four types of rope brake devices are: descender device, belay device, positioning device and a fall shock absorber.

If the device is to arrest a rope, friction conditions need to be created between the rope and parts of the device. Usually, there are two variants of rope installation. In a first variant, the rope is guided through the device without folds, which allows the rope to freely move through the device when in an unloaded state; in a second variant folds over the device element surface are present that hinder a free movement of the rope through the device. In case of a rope without a fold, a high surface area pressure of the braking part of the device against the rope is required; in this case the braking force is calculated by the formula of surface area pressure with the belonging friction coefficient between the materials. The rope is loaded at individual points and therefore more exposed to damages and wear than in the case of a folded rope, where the friction force is distributed over a larger surface. T he braking force in this case is linearly proportional to the force of the surface area pressure on the rope. The braking force is defined by the coefficient of friction, the diameter of the fold of the rope, and a wrap angle of the surface contact between the rope and the sliding surface of a roller or parts of the device. T he braking force increases exponentially with the increase in the wrap angle and i n the coefficient of friction.

Ropes have various characteristics that depend on the manufacturer and the type of the rope, the thickness of the rope, wear, age and impregnation of the rope with oil, water, mud, sand. All these variables have impact on the functioning of the device. The functioning of the device is also influenced by the loading force and the loading speed of the rope. These variables have influence on the functioning of the device in various circumstances, thus reducing its safe operation. After all, reliability and safety are of key importance, so there is a need for a device that will provide for stable functioning in all conditions.

There are two possible ways of arresting the movement of a loaded rope: a odynamici possibility by the rope sliding through the device or a ostatici possibility without sliding. The dynamic braking with sliding is used in fall shock absorbers for instance. In case of the static braking of movement the pulsed force is present. T he energy gets absorbed by the stretch of the rope or more precisely by friction within the rope. There is interdependence of the loading force and the braking path in the dynamic braking of movement, while the braking force, at which the sliding occurs, changes as a function of the thickness and rigidity of the rope and of the type of the braking mechanism of the device. In this case the device absorbs part of the energy by friction between the rope and the parts of the device, while the remaining part of the energy is absorbed by the stretch and friction in the rope.

The most frequently used mechanism for the static braking of the movement of the rope through a device is a mechanism with an eccentrically fastened pivotal part of the mechanism which acts in a self-jamming manner when pressing against the rope. Such mechanism is disclosed in document DE2439678A1. A drawback of such a solution is high loading forces of the system which may lead to the ropes or parts of the system getting damaged, and high forces on a handle that acts on the eccentric wheel to unload the system. Should the movement of the eccentric wheel be limited and the rope allowed to slip, a problem of adjustment to various thicknesses of the rope occurs and this limits both the applicability and the safety of the device. In addition, the forces of the eccentric wheel pressing against the rope depend on the position of the eccentric wheel and the position depends on the rope thickness.

In the dynamic blocking of the movement of the rope by sliding through the device, a simple mechanism, through which a rope is wound, is most frequently used. Such mechanism is disclosed in document FR2631325A1 and serves as a belay device or a descender for absei I i ng.

In the field of protecting people working at heights, for sports and industrial applications, two types of fall shock absorbers are normally used. In one type a stitched web that is fold several times is used, where the stitches start tearing upon load thus absorbing the energy of the fall. This type of the shock absorber is most frequently used in industrial applications, a typical example is found in document US3444957. A drawback of this shock absorber is its single use only. A second type of the fall shock absorber is divided in two subtypes. A first subtype uses a perforated plate without movable elements, through which a rope dimensioned to the diameter of the holes in the plate is guided. An advantage is the simplicity of the design, while a drawback is the changing braking conditions which depend on the changes in the rope which becomes less flexible and stiff over time; this results in a higher braking force and the device is therefore dangerous for use. Such a device is disclosed in document DE3345290A1. Another subtype of the fall shock absorber uses a mechanism that allows the rope to slip under a certain force. This shock absorber is normally used both as a belay device and as a fall shock absorber simultaneously. These are self- braking safety devices for large loads as disclosed in document E P1123718A1. Advantages of this self-braking shock absorber/belay device are its possibility of being used several times, its possibility of a controlled lowering of a load, and its possibility to retain huge loads due to a large wrap angle of the rope around the pivotal part of the braking mechanism. Disadvantages are unadjustable braking force, a very limited scope of use of various rope thicknesses, hindered movement of the rope through the device when not loaded, the size, the weight and consequently high price.

Belay devices are divided in active assisted braking belay devices and passive manual belay devices, in which a climber's fall is arrested by way of manually retaining the rope at the input side of the device. Assisted braking belay devices usually apply an eccentric cam brake mechanism as disclosed in document US5076400A. These assisted braking devices jerkily arrest a fall which is unpleasant for a climber and may be dangerous for the person who protects as well since the force of the rope lifts him from the ground when the climber free fall is severe, whereby he can hit against a rock. Huge forces are also problematic for running belays that a climber makes in deep cracks while climbing. An advantage of the assisted braking devices lies in the fact that the rope does not slip through the device when the rope is not retained by a hand, wherewith a climber's free fall and a hit against an obstacle are prevented. As these devices provide for a higher level of safety, they are preferred although they are more expensive, larger, heavier and use a mechanism which is not sufficiently reliable in certain circumstances. This latter fact is undesired characteristics of the device. A device that functions in a assisted braking way and allows the rope to slip at lower forces is disclosed in document US 2003196853A1. Although providing for automatic braking, these devices so not provide for perfect safety since it may happen that the mechanism will not detect a fall and consequently arrest rope sliding. During protection, the climber must thus never let the rope out of his hand. An example of a device that solves this problem by way of a centrifugal cam-clutch that detects a fall based on the acceleration rate of the rope through the device is disclosed in document US2014262611A 1.

Other passive belay devices, with which a climber's fall is arrested by way of a manual retention of the rope, provide for dynamic protection or osofti arresting of the fall. This is made possible by a manually controlled slip of the rope through the device. Such a device is disclosed in document US D5938 4. As these devices have a relatively small braking force, the fall is very difficult to retain in case of a huge fall. Since the forces of such fall can exceed the forces that can be retained by a hand, the climber's fall can be fatal or the person who protects the climber can get his hand injured due to retaining the rope. Improvements made to increase the braking power of the device are achieved by a larger V groove that functions in a partly self-jamming manner as disclosed in document US2011284323A 1; however, there still remains a danger of releasing the rope from one's hand. Moreover, the device is rather aggressive with regard to the rope as the rope gets worn especially in case of abseiling.

The passive belay devices which dynamically arrest the rope typically allow free sliding of the rope through the device when the latter is unloaded, while the assisted braking belay devices considerably hinder this movement of the rope and trigger the braking mechanism more rapidly and more frequently especially when the rope is briskly pulled. T his is disturbing for the climber since it hinders him in climbing. To eliminate this problem a variety of techniques of manual retaining of the braking mechanism are in use; however, this increases a possibility of the device not to detect a fall and the person who protects the climber instinctively fails to set the retaining of the braking mechanism free which reduces the safety of the safety device. Both types of devices have advantages and disadvantages. An advantage of one of them is a disadvantage of another one and vice versa, so there is a need for a device that would combine good properties of both types of devices. An attempt to join dynamic and static protection in one single device is disclosed in document US2014174850.

The fundamental function of the brake is a controlled abseiling. T he self-jamming rope descenders normally use an eccentric braking mechanism and this is why the rope slides through the devices only at high forces, depending on rope thickness, between 4 kN and 9 kN. An example is evident from US5054577A.

Positioning devices are used to position a worker at a height, for instance on an electric pole or on a roof, wherein the rope system is adjusted to a certain distance which limits the movement and thus prevents the person from falling. An example of such a device is disclosed in document US8464832B1.

T echnical Problem

The technical problem is how to conceive a rope brake device that will be simple in construction, small-size, light-weight and price efficient for manufacturing. The goal is to conceive a plurality of rope brake devices with a single constructional concept. By changing certain constructional parameters, the devices will meet the requirements for belay devices, descenders, rope shock absorbers and positioning devices. Further, the rope brake device should provide for double-sided operation, operation with a large range of rope thicknesses and stiffness, smooth sliding of the rope through the device when the rope is unloaded and automatic triggering of the brake mechanism upon an impulse load or when the rope slides through the device at a more accelerated rate. The device should further allow for controlled unloading. Solution to the T echnical Problem

The technical problem is solved by a rope brake device comprising:

- a substantially plate-shaped basic element that further comprises an upper section of the basic element provided at the upper part with a first hole to receive both ends of a rope, and a bottom section of the basic element,

- an axle fixedly connected with the bottom part of the upper section of the basic element in a way to form an angle a with the upper section of the basic element in a longitudinal cross-section,

- a pivotal element that is pivotal ly, preferably centrally arranged on the axle and around which a rope is guided, and

- a push element, preferably a cylindrical one, that is fixedly connected with a circumferential part of the pivotal element in a way to project from said element upwards, wherein the axis of the pivotal element and the axis of the push element enclose an angle b.

The rope brake device comprises a second hole for receiving a karabiner that is optionally arranged at the bottom part of the bottom section of the basic element or on a holder arranged in the axis of said axle.

When the rope brake device is in the operating position, the rope is guided from the upper side through the first hole, around the pivotal element and back through the first hole from the bottom side. The direction, from which the rope is introduced into the device, is irrelevant since the device has a double-sided operation. When the rope is unloaded it freely slides through the rope brake device. When one end of the rope is loaded by an impulse or when the sliding velocity of the rope is considerably accelerated, the pivotal element rotates due to the friction between the rope and the pivotal element, wherein the push element pushes the rope against the internal surface of the upper section of the basic element and brakes the sliding of the rope through the rope brake device. The rope brake device can further comprise a ball, a spring or a locking element that are arranged within a third through hole formed in longitudinal direction of the push element. In an unloaded state of the rope brake device, the ball which is loaded by a biased spring engages with a fourth hole formed in an element, on which the pivotal element is arranged and prevents the rope brake device from getting activated too rapidly, i. e. when the rope freely slides through the device. When the velocity of the rope through the rope brake device increases, the friction between the rope and the pivotal element pushes the ball against the force of the spring from its locked position and the pivotal element can rotate around its axis.

T he braki ng force depends on the wrap angle g of the rope. T he larger the angle g the higher the braking force. The wrap angle of the rope determines a ratio between the diameter d of the pivotal element and the width a of the first hole. Remaining mechanisms used to i ncrease the braki ng force wi 11 be explai ned i n the conti nuation.

The end sections along the longitudinal side of the basic element mutually enclose an angle w.

Various configurations of the rope brake device are possible. Parameters are selected as to which function of the device is preferred, i. e. as a function of the purpose of the device.

One of possible configurations of the constructional parameters of the rope brake device is a configuration, in which the angles a and b are identical and measure substantially 90e The angle w is substantially 180e. The push element moves in parallel to the internal surface of the basic element. The push element when loaded, pushes the rope against the internal surface of the basic element or against an edge of the first hole as a function of a distance b of the push element from the internal surface of the basic element and of the rope thickness. In fact, the distance b determines the brake force which depends on the rope thickness. Such embodiment of the rope brake device is suitable especially as a rope descender, as a positioning device or as a fall shock absorber.

A second one of possible configurations of the constructional parameters of the rope brake device is a configuration, in which the angles a and b are identical and are larger than 60e and smaller than 90e The angle w is twofold the angle b. The internal surface of the basic element is an approximation of a curved surface of a truncated cone, the centre line of which is aligned with the axis of the pivotal element, such that the push element moves parallel to the internal surface of the basic element. The push element when loaded, pushes the rope against the internal surface of the basic element or against an edge of the first hole as a function of a distance b of the push element from the internal surface of the basic element and of the rope thickness. In this case too, the distance b determines the brake force which depends on the rope thickness. Such embodiment of the rope brake device is functionally similar to the first embodiment but is much more sophisticated in design and more suitable for handling from the point of view of ergonomics. It is suitable especially as a positioning device, as a rope descender or as a fall shock absorber.

A third possible configuration of the constructional parameters of the rope brake device is a configuration, in which the angle a exceeds 904 is preferably between 100e and 110 and the angle b measures between 60e and 90έ, preferably 90e. The angle w measures between 90e and ^* \80έ, preferably between 110e and 130e A larger angle a means a larger braking force. Here, the push element does not move parallel to the internal surface of the basic element. Once the pivotal element is rotated, a wedge- 1 ike space is formed between the push element and the internal surface of the basic element, in which wedge-like element the rope to be decelerated is jammed. The wedge-like space in this embodiment adapts to various rope thicknesses. The braking force is maintained regardless of the rope thickness. Such embodiment of the rope brake device is suitable especially as a belay device. If the device is provided with a deflector element that is described in the continuation, it is suitable also for application as a positioning device, a rope descender or a fall shock absorber.

In order to increase the braking force of the rope brake device, the pivotal element can be provided with a first deflector element on the side opposite the push element. T he first deflector element deflects the rope guided around the pivotal element in a plane transversal to the axis of the pivotal element by a distance c from the internal surface of the basic element. The braking force is further increased if the first deflector element is formed at an angle, such that the angle d between the axis of the pivotal element and the axis of the first deflector element is smaller than 90 , is preferably between 60e and 80e

A lternatively, the rope brake device may comprise a second deflector element integrally formed with the basic element on the internal side on the upper part of the lower section of the basic element. T he second deflector element causes the rope to be spaced from the internal surface of the basic element by a distance c. Its function is similar to that of the first deflector element but the impact on the increase of the braking force is poorer. T he braking force is further increased if the second deflector element is formed at an angle, such that the angle d between the axis of the pivotal element and the axis of the second deflector element is smaller than 90 , is preferably between 60e and 80e

T he device further comprises a discharge handle that allows a manually controlled unloading of the rope brake device i n the event of descending.

T he upper end of the basic element may be provided with a groove i n the longitudinal direction of the basic element. T he groove is intended to receive the free end of the rope. T he rope is folded over the groove, wherewith the braking force of the climber at controlled abseili ng is increased and the braking control i mproved. The advantage of the rope brake device of the invention over known devices is its simple construction with a small number of parts, its small size and low weight as well as low production costs. By changing certain parameters, a single constructional concept allows for manufacturing of a device that meets the requirements of an international standard for belay devices, brakes, rope fall shock absorbers and positioning devices. A further advantage is a double-sided operation of the rope brake device, wherewith a fatal mistake in guiding the rope through the device is eliminated. A further advantage of the rope brake device over known devices is also its huge insensitivity to various rope thicknesses and hardnesses since it allows for optimal operation of the device by using a wide scope of various rope thicknesses. It allows a smooth sliding of the rope through the device when the rope is not loaded and automatic triggering of the brake mechanism upon an impulse load or in case of an accelerated sliding rate of the rope through the device (e. g. above 1 m s). A further important advantage of the rope safety device of the invention is that the brake is activated in each situation, also in the event when the free end of the rope is not retained by a hand.

Figure 1 : prior art rope brake devices: a. self-jamming device, b. self-jamming eccentric brake, c. conical positioning device, d. eccentric positioning device, e. manual brake with rollers, f. fall shock absorber with a perforated plate, g. manual brake (figure eight descender), h. tubular manual belay device;

Figure 2: two ways of using the rope brake device of the invention while used as a belay device;

Figure 3: rope brake device with a first deflector element in which the angles a and b amount to 90e and the angle w is 180e;

Figure 4: rope brake device with a holder and a mechanism against a too rapid triggering of the rope brake device;

Figure 5: rope brake device with a holder and a mechanism against a too rapid triggering of the rope brake device in cross-section; Figure 6: rope brake device with a holder and a first deflector element, in which the angles a and b amount to 90e and the angle w is 180e;

Figure 7: rope brake device with a holder and a second deflector element, in which the angles a and b are smaller than 90e and the angle w is smaller than 180e;

Figure 8: rope brake device with a holder, in which the angle a is larger than 904 the angle b is 90e and the angle w is smaller than 180e;

Figure 9: illustration of adjustment of the rope brake device to various rope thicknesses;

Figure 10: a rope in the rope brake device in an unloaded state;

F igure 11 : a rope i n the rope brake devi ce i n a I oaded state;

Figure 12: eccentric arrangement of a pivotal element;

Figure 13: rope brake device with lateral stops.

The invention is described in more detail in the continuation.

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

- a substantially plate-shaped basic element 2 that further comprises an upper section 2a of the basic element provided at the upper part with a first hole 3 to receive both ends of a rope 6, and a bottom section 2b of the basic element,

- an axle 4 fixedly connected with the bottom part of the upper section 2a of the basic element in a way to form an angle a with the upper section 2a of the basic element in a longitudinal cross-section,

- a pivotal element 5 that is pivotal ly, preferably centrally arranged on the axle 4 and around which a rope 6 is guided, and

- a push element 7, preferably a cylindrical one that is fixedly connected with a circumferential part of the pivotal element 5 in a way to project from said element upwards, wherein the axis of the pivotal element 5 and the axis of the push element 7 enclose an angle b. The pivotal element 5 is preferably cylindrically shaped but may also have a shape of a truncated cone. It may have a polygonal cross-section (for instance square shaped), but free sliding of the rope through the rope brake device in an unloaded state is hindered in this case. The pivotal element 5 can be arranged on the axle 4 eccentrically, yet the braking force will be higher and the device will brake statically without sliding.

The pivotal element 5 can be mounted by means of a ball bearing, a roller bearing, a needle bearing or by means of a bearing bush or a combination thereof (e. g. a combination of a ball bearing and a plastic bearing bush).

The rope brake device comprises a second hole 8 for receiving a karabiner 17 that is optionally arranged at the bottom part of the bottom section of the basic element or on a holder arranged in the axis of said axle 4. The holder may be realized in any known constructional way. It may be integrally shaped with the axle, it may be arranged on said axle by means of a pin 11 projecting through said axle, etc. T he pivotal element can be arranged on the axle with an intermediate arrangement of a sliding bushing.

When the rope brake device 1 is in the operating position, the rope 6 is guided from the upper side through the first hole 3, around the pivotal element 5 and back through the f i rst hole 3 from the bottom side.

The rope brake device 1 can further comprise a ball 12, a spring 13 and a locking element 14 that are arranged within a third through hole 15 formed in longitudinal direction of the push element 7. In an unloaded state of the rope brake device 1, the ball 12 which is loaded by a biased spring 13 engages with a fourth hole 16 formed in a constructional part, on which the pivotal element 5 is arranged and prevents the rope brake device 1 from getting activated too rapidly, i. e. when the rope freely slides through the device. When the rope freely slides through the rope brake device there is not much friction between the rope 6 and the pivotal element 5. When the velocity of the rope through the rope brake device increases due to a fall or due to the rope getting folded over the device or due to the rope getting off the hand, the friction between the rope and the pivotal element increases as well and the latter pushes the ball 12 against the force of the spring 13 from its blocked position. The pivotal element 5 rotates around its axis. Said mechanism is not only activated in the event of a brisk load but also in the event when the velocity of the rope through the device increases gradually, which is important for a safe operation of the device.

T he braki ng force depends on the wrap angle g of the rope. T he larger the angle g the higher the braking force. The wrap angle of the rope determines a ratio between the diameter d of the pivotal element 5 and the width a of the first hole 3. The wrap angle g of the rope and herewith the braking force which increases exponentially with the increase of the wrap angle, are influenced by the rope thickness. A thinner rope means a smaller wrap angle g.

The end sections along the longitudinal side of the upper section 2a of the basic element mutually enclose an angle w.

Constructional parameters of the rope brake device are selected as to which function of the device is preferred, i. e. as a function of the purpose of the device.

According to one of the embodiments of the rope brake device 1 the angles a and b are identical and measure substantially 90e. The angle w is substantially 180e The push element 7 moves parallel to the internal surface of the basic element 2. The push element 7, when loaded, pushes the rope 6 against the internal surface of the basic element 2 or against an edge of the first hole 3 as a function of a distance b of the push element 7 from the internal surface of the basic element. The distance b determines the braking force which depends on the rope thickness. Such embodiment of the rope brake device is suitable especially as a descender, as a positioning device or as a fall shock absorber. According to a second embodiment of the rope brake device the angles a and b are identical and measure between 60e and 90e, preferably between 70e and 80e T he angle w is twofold the angle b. T he internal surface of the basic element is an approximation of a curved surface of a truncated cone, the centre line of which is aligned with the axis of the pivotal element 5, such that the push element 7 moves parallel to the internal surface of the basic element 2. T he push element 7, when loaded, pushes the rope 6 against the internal surface of the basic element or against an edge of the first hole 3 as a function of a distance b of the push element 7 from the internal surface of the basic element 2. In this case too, the distance b determines the brake force which depends on the rope thickness. Such embodi ment of the rope brake device 1 is functionally si milar to the first embodiment but is much more sophisticated in design and more suitable for handling from the point of view of ergonomics. It is suitable especially as a positioning device, as a descender or as a fall shock absorber.

T he rope brake device 1 further comprises a li miter 21 of the pivotal movement of the pivotal element. It is formed as a projecting element arranged on the basic element, against which the push element 7 leans in the loaded state of the rope brake device, wherewith the push element is prevented from further movement. Of course, the I i miter can be formed in any constructional manner.

According to a third embodiment of the rope brake device 1 the angle a exceeds 90έ, it is preferably between 100e and 1104 and the angle b measures between 60e and 110e\ preferably between 60e and 90 , is more preferably 90e T he angle w measures between 90e and ^* \ 80έ, preferably between 110e and 130e. A larger angle a means a larger braking force. Here, the push element 7 does not move parallel to the internal surface of the basic element. Once the pivotal element 5 is rotated, a wedge- 1 ike space is formed between the push element 7 and the internal surface of the basic element 2, in which wedge-like element the rope 6 to be decelerated is jammed. T he wedge-like space in this embodi ment adapts to various rope thicknesses. T he braking force is mai ntained regardless of the rope thickness. Such embodi ment of the rope brake device 1 is suitable especially as a belay device. When the rope brake device is used as a belay device, the two embodiments, in which a = 1104 b = 90e and w =1304 or a = '\ '\ 0έ, b = 80e and w =120e prove to be an opti mal combination of parameters. In such configuration of the rope brake device dynamic braking with the rope slide is achieved. T he self-jamming of the device is provided for and this is i mportant for safety. T he braking force can be influenced by manual retaining of the rope, wherein a quite small retaining force of the rope by a hand considerably i ncreases the braking force of the device. T he rope thickness has no significant impact on the braking force. T his is true for rope thicknesses which are normally used in belay devices, i. e. from 7.5 mm to 11 mm, and i n brakes from 10 mm to 13 mm.

In addition, a variant of the third embodiment is defined, where the angle w =180e. In this embodi ment, the rope brake device may be provided with two axial ly symmetrical lateral stops that are formed each time by an upper lateral stop surface M and a bottom lateral stop surface P. T he upper lateral stop surface M intersects the surface of the upper section 2a of the basic element at an angle e between Oe and 30έ, preferably ^* \ 0έ, with respect to the longitudinal axis of the rope brake device 1. T he upper lateral stop surface M is elevated from the plane of the surface of the upper section 2a of the basic element by an angle r that measures between 20e and 70έ, preferably 45e. T he upper lateral stop surface M passes at the bottom end into the bottom lateral stop surface P which intersects the surface of the upper section 2a of the basic element at an angle t between 30e and 90έ, preferably 45¾ with respect to the longitudi nal axis of the rope brake device 1, wherein said intersection is remote from the centre of rotation of the pivotal element by a distance n. T he bottom lateral stop surface is elevated from the plane of the surface of the upper section 2a of the basic element by an angle f that measures between 30e and 70έ, preferably 45e T he bottom lateral stop surface P passes at the bottom end through a truncation to a conical surface S that forms an angle I with the axis of the pivotal element, said angle measuring between 40e and 60έ, preferably 50e T he lateral stop surface, against which the push element pushes the rope 6 when in the operating state, limits the rotation of the pivotal element 5 and consequently the braking force at a fall.

The rope brake device 1 can further comprise a limiter of the pivotal movement of the pivotal element. It is formed as a projecting element arranged on the basic element, against which the push element 7 leans in the loaded state of the rope brake device, wherewith the push element is prevented from further movement. Of course, the limiter can be formed in any constructional manner.

In order to increase the braking force of the rope brake device, the pivotal element 5 can be provided with a first deflector element 9 on the side opposite the push element, said deflector element 9 being arranged at an angle d with respect to the axis of the pivotal element 5. The first deflector element 9 deflects the rope 6 guided around the pivotal element 5 in a plane transversal to the axis of the pivotal element by a distance c from the internal surface of the bottom section 2b of the basic element. The braking force is further increased if the first deflector element 9 is formed at an angle, such that the angle d between the axis of the pivotal element 5 and the axis of the first deflector element 9 is smaller than 90έ, is preferably between 60e and 80e. The device provided with the first deflector element 9 is suitable as a positioning device, a descender or a fall shock absorber. Of course, when the rope brake device is realised by a conical surface S, the shape of the first deflector element 9 is adapted in a way not to collide with the conical surface S.

Alternatively, the rope brake device may comprise a second deflector element 18 integrally formed with the basic element on the internal side on the upper part of the lower section 2b of the basic element. The second deflector element 18 causes the rope to be spaced from the internal surface of the bottom section 2b of the basic element by a distance c. Its function is similar to that of the first deflector element 9 in that the deflector element determines the position of the rope in the rope brake device and herewith the sliding of the rope through the device, yet the braking force is smaller in this case. The braking force is further increased if the second deflector element is formed at an angle, such that the angle d between the axis of the pivotal element and the axis of the second deflector element is smaller than 904 is preferably between 60e and 80e

The distance c impacts the size of the braking force but also the sliding of the rope through the rope brake device when the rope is in the unloaded state. In fact, it is selected as a function of the desired characteristics of the rope brake device.

The device further comprises a discharge handle 25 that is connected with the pivotal element 5 and allows a manually controlled unloading of the rope brake device in the event of abseiling. The connection can be direct or via lever.

The upper end of the basic element may be provided with a groove 19 in the longitudinal direction of the basic element 2. The groove 19 is intended to receive the free end of the rope 6. The rope can be folded over the groove, wherewith the braking force of the climber at abseiling is increased and the braking control improved.

The device can further comprise a housing that is not the object of the present invention.