EP3883875A1

EP3883875A1 - Speed limiter for a lifting gear having brake actuated by centrifugal force

Info

Publication number: EP3883875A1
Application number: EP19806195.4A
Authority: EP
Inventors: René HOLZER; Leopold Latschbacher; Christoph RUSSWURM
Original assignee: Wittur Holding GmbH
Current assignee: Wittur Holding GmbH
Priority date: 2018-11-19
Filing date: 2019-11-19
Publication date: 2021-09-29
Also published as: CA3120016A1; WO2020104428A1; CN113039144A; DE202019105089U1; CN113039144B; AU2019385636A1; US20210387831A1; JP7437595B2; JP2022507626A; US11814265B2

Abstract

The invention relates to a speed limiter for a lifting gear comprising a sheave driven by a speed limiter cable and a brake for braking the sheave, wherein the brake comprises at least one eccentric piece, mounted on the sheave in a pivoting manner, wherein the eccentric piece is mounted on a first centrifugal weight in a pivoting manner and mounted on a second centrifugal weight in a pivoting manner, wherein, in the event of a displacement of the first and second centrifugal weights due to centrifugal force, the first and the second centrifugal weights pivot the eccentric piece, the brake comprising a reset unit having a spring system which pulls the centrifugal weights in the direction of the undeflected position thereof, wherein the spring system has a first spring constant up to a switching speed, the spring system has a second spring constant from the electric switching speed of the sheave and the second spring constant is greater than the first spring constant.

Description

SPEED LIMITER FOR A LIFT WITH

Centrifugal brake

THE TECHNICAL GENERATION

The invention relates to a speed limiter according to the preamble of claim 1 and a conveyor with a car guided on guide rails and a

corresponding speed limiter.

THE TECHNICAL BACKGROUND

Such speed limiters are used in particular in cable and cable hydraulic elevators to activate a braking and / or safety device as soon as the car moves in an impermissible manner or in an impermissibly fast manner. The term "car" is to be interpreted broadly and covers all types of cabins, load carriers, load-carrying platforms and the like.

A variety of known speed limiters

are based on the principle of the centrifugal brake.

Here are usually a pulley and with

Connected centrifugal weights are provided, which are in the undeveloped state of the rope pulley in an undeflected

Position and are driven radially outwards as the speed increases due to the centrifugal force. A single centrifugal weight is held by a spring, the spring force exerted by the spring counteracting the centrifugal force. On the one hand, the spring serves to reduce the speed when the speed drops

Bring the flyweights back to the undeflected position. The spring, on the other hand, serves the travel of the

Reduce flyweights. Modern speed limiters usually detect at least two speeds, both above the

Nominal speed, i.e. the usual operating speed of the hoist. The speeds to be detected are one electrical switching speed and one

mechanical switching speed that is greater than the electrical switching speed. The switching speeds are each measured via the deflection of the centrifugal weights, the deflection depending on the spring force and the centrifugal force. When the electrical switching speed is detected, the travel speed of the hoist is reduced by electrical means, in particular the drive motor. At

Detection of the mechanical switching speed, the safety gear of the hoist is switched on.

The problem with the known speed limiters with centrifugal brake is that the centrifugal force

proportional to the distance of the flyweight from the axis of rotation of the flyweight and quadratic to the increasing

Rotation speed increases, so with conventional

Speed limiters increase the sensitivity of the detection of the switching speed. This makes it very difficult to set the means for the detection of the electrical and mechanical switching speed.

THE TASK BASED ON THE INVENTION

It is therefore the object of the invention, one

To create speed limiters that are easy

can be adjusted.

This object is achieved with a speed limiter with the features of claim 1. Accordingly, a speed limiter for a hoist, in particular an elevator installation, is provided, which in turn rotates from one around a main axis (H)

Speed limiter rope driven pulley and a brake for braking the pulley includes. The brake includes at least one pivotable on the rope sheave

stored eccentric and a first flyweight and a second flyweight. The eccentric piece is pivotally mounted on the first centrifugal weight and pivotably on the second centrifugal weight, with the first and second centrifugal weights pivoting the first and second centrifugal weights when the first and second centrifugal weights are displaced. The brake includes a return unit with a spring system that the

Flyweights with the one provided by the spring system

Pulls spring force towards its undeflected position.

The spring system has up to (= preferably exactly "up to", in the wider sense in the range up to + 25% better only + 10% ideally only + 7.5% below or above) one

electrical switching speed of the pulley a first spring constant and from the electrical

Switching speed of the pulley a second spring constant. The second spring constant is larger than the first spring constant. In particular, the second

Spring constant by a factor of about 1.05, expediently by a factor of about 1.5, particularly expediently by a factor of about 2 greater than the first spring constant.

Ideally, the second spring can be preloaded in order to produce an immediate increase in the characteristic curve with a subsequently flat characteristic curve as soon as the spring is actuated.

In this way, a nonlinear and / or discontinuous, in particular sectionally linear,

Spring characteristic curve reached, the spring force with greater deflection, especially from the electrical

Switching speed, due to the non-linearity and / or Discontinuity increases more compared to one

Spring characteristic curve at which the spring constant is constant over the entire deflection. This will occur at high

Speeds with high centrifugal forces also high spring forces. In addition, the two trigger points of the can by independent selection of the two spring constants

Speed limiter can be easily set independently. In particular, the setting of the means for the detection of electrical and mechanical

Switching speed is very easy.

The first spring constant is expediently constant. The second spring constant is expediently constant. Thereby

commercially available, inexpensive springs can be used. In addition, it is very easy to set the means for the detection of the electrical and mechanical switching speed with a constant spring constant.

FURTHER EMBODIMENTS OF THE INVENTION

The spring system advantageously comprises a first spring with the first spring constant and a second spring, the second spring constant resulting from an interaction, in particular from addition, of the spring constants of the first and the second spring. The second spring expediently exercises up to

When the electrical switching speed is reached, no force is exerted on the flyweights. By the two independent

Springs can set the trigger points for the electrical and mechanical switching speed particularly well and easily.

Alternatively, a spring system could also be used, in which the spring system consists of a single spring, the individual spring having sections of the first and the second spring constant. Such an individual is expedient Spring a coil spring, especially a tension or

Compression spring. Such a single spring can be a conical spring, in particular conical. Alternatively, such a single spring can be designed so that individual

Spring sections are depending on the force acting on the block. By using only a single spring, the construction is simplified and possibly particularly compact.

The first spring is preferably designed as a compression spring and is supported on one spring end on the first centrifugal weight, the spring on the other spring end being supported on a spring support, and the spring support on the second

Centrifugal weight is operatively connected. This makes them both

Centrifugal weights coupled together via the spring.

The second spring is expediently a tension spring, the second spring on one spring end on the first centrifugal weight

attached, in particular is attached, and wherein the second spring at the other spring end is attached to the second centrifugal weight, in particular is attached.

The second spring is advantageous as a leg spring, too

Called torsion spring, designed, wherein one leg is supported on the eccentric piece, and the other at the latest from the electrical switching speed

Leg is supported on one of the two flyweights. In a further embodiment, one leg can be supported on one of the two flyweights, and the eccentric piece is supported at the latest from the electrical switching speed of the other leg.

Preferably, a stop pin is ideally provided with an elongated hole on one of the flyweights, and the stop pin or the elongated hole serve as a stop for the second spring. It is useful until the stop touches the second spring, in particular a leg of the second spring, a certain travel path is provided. In particular, the second spring, in particular a leg of the second spring, only touches the stop from the electrical switching speed.

This increases the closing force, which acts against the

Centrifugal force acts.

The stop pin is useful as an eccentric pin

executed. As a result, the time at which the leg spring becomes active can be set simply and precisely by rotating the eccentric bolt.

The second spring is advantageously biased. As a result, when the second spring comes into effect, a quasi-sudden increase in the spring characteristic can be generated, which further optimizes the distance savings in the centrifugal weights. In addition, the second spring can have a comparatively flat spring characteristic, that is to say a comparatively small spring constant,

in particular with a spring constant that is smaller than the spring constant of the first spring, and yet in particular to exert the required force. As a result, after the sudden increase in the spring characteristic, induced by the pretensioning of the second spring, a flat spring characteristic is again provided. This makes it easy to set the range without any particular sensitivity.

The second spring is preferably attached to a spring holder which is adjustably attached to the eccentric piece, wherein

especially the bias of the second spring

Adjustment of the spring holder is adjustable. Through the

Adjustment of the attachment allows the spring preload to be changed and the system to be easily adjusted.

One end of the second spring can expediently be moved in an elongated hole up to the electrical switching speed, the elongated hole being arranged in particular in one of the two flyweights. No force is transmitted from the spring. Are the flyweights due to the

If centrifugal forces travel far enough, the spring in particular lies against the end of the elongated hole and the spring transmits

Powers. This makes it easy to ensure that the second spring does not transmit any forces up to the electrical switching speed.

The brake advantageously comprises two pivotable on the

Rope pulley mounted eccentric pieces, each of the

Eccentric pieces pivotable on the first flyweight and

is pivotally mounted on the second centrifugal weight, the first and second centrifugal weights being the case of a centrifugal force-related displacement of the first and second centrifugal weights

Swing eccentric pieces, the first spring consisting of two first, in particular identical, individual springs, each of the first individual springs being supported at one spring end on one of the two flyweights and each of the first individual springs being supported on a spring support at their other spring ends, the two first single springs over the

Spring support are operatively connected to each other, and wherein the second spring consists of two second, in particular

identical in construction, there are individual springs, with each of the second individual springs being supported at one spring end on one of the two flyweights and at their other spring ends in each case on an eccentric piece, in particular from at least the electrical switching speed.

The first spring is preferably biased. The first spring is expediently preloaded to such an extent that up to somewhat above, in particular about 10%, expediently about 5%, particularly

Appropriately about 2% - 3% of the nominal speed, that is the usual operating speed of the hoist, no movement of the flyweights from the undeflected position due to the Centrifugal force. This allows the construction to be carried out in a particularly space-saving manner. In addition, the means for detecting the electrical switching speed can be set particularly easily.

It is expedient to use a conveyor with a car guided on guide rails, a drive system and a braking device which interacts with the guide rails

Ending an impermissible state of movement of the car and a speed limiter according to one of claims 1 to 14 for triggering the braking and catching device

intended .

Other advantages, modes of action and

Embodiments of the invention result from those described below with reference to the figures

Embodiments.

FIGURE LIST

Show it:

Fig. 1: schematic view of a partially assembled

Speed limiter as

Overview display,

Fig. 2: a front view of the partially assembled

Speed limiter with rope pulley in a first embodiment with flyweights in an undeflected position,

2a shows an enlarged detail from FIG. 2 Fig. 3: a front view of the partially assembled

Speed limiter in the first

Embodiment, wherein the rope pulley rotates at an electrical switching speed,

Fig. 4: an exploded view of the partially assembled

Speed limiter in the first

Embodiment,

Fig. 5: a schematic view of an assembled

Speed limiter,

Fig. 6: a front view of the partially assembled

Speed limiter with rope pulley in a second embodiment with flyweights in an undeflected position,

Fig. 7: a perspective view of the partially assembled

Fig. 8: a front view of the partially assembled

Speed limiter in the second

Embodiment, wherein the rope pulley rotates at the electrical switching speed,

Fig. 9: a front view of the partially assembled

Speed limiter in the second

Embodiment, wherein the rope pulley rotates at a mechanical switching speed,

10 is a detailed view in the area of an eccentric piece, the sheave rotating at a mechanical switching speed, 11: a detailed view in the area of an eccentric piece, the rope pulley not rotating,

Fig. 12: an exploded view of details in the area of the

Eccentric piece,

Fig. 13: a front view of the partially assembled

Speed limiter with rope pulley in a third embodiment, the

Pulley with the electrical

Switching speed rotates,

14: a perspective view of the partially assembled

Speed limiter in the third

Embodiment, wherein the rope pulley rotates at the electrical switching speed,

15: a detailed view in the area of centrifugal weights, the rope pulley rotating at the electrical switching speed,

16: a detailed view in the area of the eccentric piece, the rope pulley rotating at the electrical switching speed,

Fig. 17: a schematic diagram to illustrate the

Centrifugal force at the flyweight above one

Elevator speed,

Fig. 18: a schematic diagram to illustrate a

Spring characteristic with a spring constant and a preloaded first spring, Fig. 19: a schematic diagram to illustrate a

Spring characteristic with different spring constants in sections and a preloaded first spring,

Fig. 20: a schematic diagram to illustrate a

Spring characteristic curve with different spring constants in sections and preloaded first and second springs.

THE PREFERRED EXEMPLARY EXAMPLES

FIRST EMBODIMENT

1 shows part of a speed limiter 1. The speed limiter 1 is preferably designed for vertical elevators (not shown in the figures) for the transportation of people and / or goods, but can optionally be used for other similar lifting devices or

Conveyor systems are used, the traversing movement of a permanent monitoring for detection of impermissible

Driving conditions required.

Ideally, if not necessarily, is

In terms of its basic concept, speed limiter 1 is configured in the same way as that already known from the earlier patent application DE 10 2007 052 280 by the same applicant

Speed limiter. The mentioned patent application is made by reference in its entirety to the disclosure component of the description here, so that the basic function and the basic structure of what is preferred here

The speed limiter described in the exemplary embodiment does not have to be retold. Takeover of

Delimitation features from the existing application text are reserved. The speed limiter 1 has a support structure 2, which here consists of an L-shaped steel plate. A stub axle 3 projecting on one side is fastened to this steel plate.

The stub axle 3 gives the main axis H of the

Speed limiter 1 before. On this stub axle 3, the pulley 4 is rotatably mounted for a speed limiter cable, not shown in the figures.

In addition to the pulley 4 is a brake rotor 5 on the

Axle stub 3 attached. This brake rotor 5 has a disk-like shape here, but in the present case it nevertheless acts like a drum brake, since its peripheral surface represents the friction surface.

The pulley 4 is on one end with

Bearing pin 6 provided. These bearing bolts 6 each form a secondary axis N, typically arranged parallel to the main axis H. An eccentric piece 7a or 7b is rotatably mounted on each of them. An eccentric disk, an intermediate piece or the like can also be regarded as an eccentric piece 7a, 7b. Each of these eccentric pieces 7a, 7b forms - possibly

equipped accordingly, which is not shown here - functionally a brake shoe. If the respective eccentric piece 7a, 7b rotates far enough, there is a braking system on the brake rotor 5. Most of the time (this is not figurative

shown) design so that the braking effect increases itself as soon as there is a first frictional contact with the by the sufficiently wide rotation of the eccentric 7a, 7b

Brake rotor has come. In order to achieve a lateral force compensation, at least two are expediently

Eccentric pieces 7a, 7b which are diametrically opposed are provided. Modified embodiments with three, four or more eccentric pieces 7a, 7b are conceivable, but are not shown here.

Each of the eccentric pieces 7a, 7b is in turn two

Coupling bolts 2200 provided, Fig. 4. Coupling bolt bores 220 are provided in the eccentric pieces 7a, 7b for the coupling bolts 2200, cf. 1. The eccentric disk 7a, 7b in question is connected via one of its coupling bolts 2200 to a first centrifugal weight 8a shown in FIG. The one in question stands above the other of its coupling bolts 2200

Eccentric disc 7a, 7b in connection with a second centrifugal weight 8b. This can be clearly seen from FIG. 2.

From the point of view of patent law, it should be noted that the terms "first eccentric" and "second

Eccentric piece "as well as" first centrifugal weight "and" second

Centrifugal weight "etc. do not initially represent a numerical restriction. However, the use of only two eccentric pieces, two centrifugal weights etc. is a preferred one

Embodiment, since it keeps the component expense small.

If necessary, it can be expedient to provide only one centrifugal weight 8a, 8b and / or only one eccentric piece 7a, 7b.

It may be appropriate to have more than two

To provide centrifugal weights 8a, 8b and / or more than two eccentric pieces 7a, 7b.

The two flyweights 8a and 8b are in this

Embodiment designed as half disks. In

In certain cases, the inherent mass of these half disks, which are preferably made of sheet metal, is sufficient for sufficient

To develop centrifugal forces at those speeds at which the response is intended to take place. In other cases, these half disks can be provided with additional weights. Neither of the two flyweights 8a, 8b is itself directly opposite the main axis H or on the stub shaft 3

stored. Instead, the centrifugal weights are held in their position exclusively with the aid of the eccentric discs 7a and 7b, with which they are coupled via the coupling bolts 2200, and with the aid of the resetting unit 10, which will be described in more detail shortly - such that the centrifugal weights 8a and 8b are sufficient high speed in radially outward

Can shift direction.

In view of FIG. 2, it is easy to understand that the centrifugal weights 8a, 8b move radially outward in opposite directions (in the direction of the arrows VR) as soon as the centrifugal force acting on them is large enough to accommodate the spring force to be explained later to overcome, which keeps the flyweights 8a, 8b in their undeflected position 9.

This creates a on the eccentric 7a and 7b

Torque, which rotates the eccentric discs or the brake pad they are not shown here so that they come into contact with the brake rotor 5 shown in FIG. 1 and, as a rule, subsequently due to the self-reinforcing effect already mentioned

Blockage occurs. As a result, the pulley 4 is braked. There is tension on the speed limiter rope. This can now be the brake or attached to it

Trigger safety gear.

It is important to make it clear that the centrifugal weights 8a and 8b shown in FIG. 2 not only shift outward in a purely radial direction, but are also subjected to a certain transverse movement, since the rotation of the eccentric discs 7a, 7b the location of the

Coupling bolts 22 holding centrifugal weights with respect to the Major axis H changes. Each of the two flyweights 8a and 8b is therefore also displaced a little in the transverse direction in the course of its displacement in the radially outward direction. This is also the reason why the two flyweights 8a and 8b are not themselves mounted directly opposite the main axis H.

Of particular interest for the invention is the

Reset unit 10. The reset unit 10 can best be described with reference to FIGS. 2, 3 and 4. The reset unit 10 comprises a spring system, which

Fly weights 8a, 8b with the spring force provided by the spring system in the direction of their undeflected position 9.

The spring system comprises a first spring. in the

2, the first spring preferably consists of two (or more) first individual springs 12a, 12b.

The first two individual springs 12a, 12b are identical

executed. In the exemplary embodiment, the first two individual springs 12a, 12b are designed as helical springs.

The first of the two first individual springs 12a is supported on its one spring end 15a on the first centrifugal weight 8a. At its other spring end 15c, the first of the two first individual springs 12a is supported on one shown in FIG. 4

Spring support 16 from. The second of the two first individual springs 12b is supported on its one spring end 15b on the second

Centrifugal weight 8b. At its other spring end 15d, the second of the first two individual springs 12b is supported on the

Spring support 16 from. The first two individual springs 12a, 12b are thus operatively connected to one another via the spring support 16.

The spring system comprises a second spring shown in FIG. 2. In the exemplary embodiment according to FIG. 2, the second spring consists of two second individual springs 14a, 14b. The second two Individual springs 14a, 14b are constructed identically. In the exemplary embodiment, the two second individual springs 14a, 14b are designed as leg springs, also called torsion springs.

There is one on each of the two flyweights 8a, 8b

Stop bolt in the form of an eccentric bolt 18a, 18b

attached. The stop bolts in the form of the eccentric bolts 18a, 18b serve as a stop for the second spring in the form of the two second individual springs 14, 14b. The first of the two second individual springs 14a can be supported on its one spring end 17a, or on one of its legs, on the second eccentric pin 18b. At its other spring end 17c, or at its other leg, the first of the two second individual springs 14a is supported on the first eccentric piece 7a. The second of the two second individual springs 14b can be on one

Spring end 17b, or on one leg, on the first

Support eccentric bolt 18a. At its other spring end 17d, or at its other leg, the second of the two second individual springs 14b is supported on the second eccentric piece 7a.

In the undeflected position 9 shown in FIG

Flyweights 8a, 8b support the one spring ends 17a,

17c of the second individual springs 14a, 14b not to the

Eccentric bolts 18a, 18b, are therefore not yet spring-loaded.

Starts the pulley 4 and thus the two flyweights 8a, 8b at a speed lower than the first

to rotate electrical switching speed, the centrifugal force emanating from the rotation and the mass of the centrifugal weights 8a, 8b presses on the first spring in the form of the first two individual springs 12a, 12b, the centrifugal force being greater than the spring force of the first spring, which is achieved by means of the first

Individual springs 12a, 12b and generated via the spring support 16 is compensated in the state of equilibrium. Preferably up to the first electrical switching speed or beyond, the spring system has a first spring constant D1, the spring constant Dl being in this

Embodiment is additively composed of the two spring constants of the first two individual springs 12a, 12b.

If the speed of the pulley 4 is increased up to a first electrical switching speed or is increased further, the eccentric pieces 7a, 7b including the second individual springs 14a, 14b fastened to the eccentric pieces 7a, 7b are pivoted until the spring ends 17a, 17b two second individual springs 14a, 14b on the eccentric bolt

18a, 18b. At a speed greater than or equal to the first electrical switching speed, the centrifugal force emanating from the rotation and the mass of the centrifugal weights 8a, 8b presses on the first spring in the form of the first two individual springs 12a, 12b, the centrifugal force being greater than the spring force of the first spring the first individual springs 12a, 12b and the spring support 16 is generated, and on the second spring in the form of the two second individual springs 14a, 14b, whereby it is compensated in the state of equilibrium. From or above the first electrical switching speed, the spring system therefore has a second spring constant D2, the spring constant D2 in this exemplary embodiment being additive from the two spring constants of the first two

Individual springs 12a, 12b and the two second individual springs 14a, 14b.

In the exemplary embodiment, all the spring constants of the individual springs 12a, 12b, 14a, 14b and thus also the first spring constant of the first spring and the second spring constant of the second spring are constant. In Fig. 4 it can be clearly seen that the eccentric bolt 18a in the form of a screw connection with a holding or

Lock nut 19 is attached to the second flyweight 8b.

The other eccentric pin 18b is in the form of an analog

Screw connection with such a nut, not shown, attached to the first flyweight 8a. The eccentric pin 18a, 18b has a slot on the head side (single or cross slot or star). This is for setting one

Screwdriver provided. The head of the eccentric pin 18a, 18b rotates eccentrically. As a result, the relative distance from the eccentric bolt to the end of the respective second individual spring 14a, 14b can easily be set. This sets the speed at which the second springs in the form of the second individual springs 14a, 14b rest on the eccentric bolt 18a, 18b and the spring constant in the overall system is increased.

Fig. 5 shows the assembly of the complete

Speed limiter 1. A means 20, in the form of a switch, is attached to the speed limiter 1. The switch is switched when the sheave 4 exceeds a predetermined speed, in particular the electrical switching speed. An electrical signal is then sent to an electronic control unit (not shown in the figures) for controlling the hoist, which causes, for example, the electric motor

is throttled so that the speed of the hoist is reduced.

If the speed of the hoist is increased even further up to the mechanical switching speed, then the

Pulley 4 braked by the brake and that around

Rope sheave surrounding rope and connected to the cabin triggers mechanical braking.

SECOND EMBODIMENT 6 to 12 show the speed limiter 1 'in a second embodiment.

The speed limiter 1 'in the second

The embodiment corresponds essentially to that

Speed limiter 1 of the first embodiment, so that what was said above about the speed limiter 1 according to the first embodiment also for the

Speed limiter 1 '' after the second

Embodiment applies except in the second

Embodiment made changes. In particular, the same reference numerals designate the same components.

The main difference of the speed limiter 1 'according to the second embodiment compared to

Speed limiter 1 after the first

Exemplary embodiment is that the second spring 13 'can be adjusted differently, more advantageously, namely mostly

more sensitive, or in a larger area.

The construction for generating the pretension of the second spring 13 'is explained below with reference to FIGS. 10 to 12 and with the aid of the second individual spring 14a' which is arranged on the first eccentric piece 7a. Corresponding statements made here can be transferred to the other second individual spring 14b ', which is arranged on the second eccentric piece 7b.

A spring holder 22 is arranged on the first eccentric piece 7a. For maintenance and adjustment, the spring holder 22 is adjustable relative to the eccentric piece 7a, for example pivotable, by means of the adjusting screw VS, cf. Fig. 10. During operation of the hoist, the spring holder 22 with the

Eccentric 7a firmly connected. In the exemplary embodiment, the spring holder 22 is produced or bent from a sheet metal, preferably. The spring holder 22 comprises a base surface 25. A particularly circular opening 26 is punched into the base surface 25, cf. Fig. 12. The opening 26 encloses the in the installed state

Coupling bolt 2200. The base surface 25 lies against a stop on the coupling bolt 2200 and is thus fixed in the axial direction, that is to say the direction parallel to the main axis H (FIG. 1). A first end surface 27 adjoins the base surface 22. The first end surface 27 is approximately 90 ° to the base surface. A receiving groove 24 is arranged in the first end surface 27. The receiving groove 24 is open towards the lower end of the end surface 27. In a further embodiment, the

Recording groove 24 also a hole, an elongated hole, or

the like.

When ready for operation, the spring end 17c, in particular the leg, of the second lies in the receiving groove 24

Single spring 14a ', cf. in particular Fig. 11.

As shown in FIG. 12, the spring holder 22 comprises a second end surface 28. The second end surface 28 is approximately orthogonal to the base surface 25 and approximately orthogonal to the first end surface 27. An edge of the second end surface 28 forms a stop 29. The stop 29 strikes when ready for operation Condition on

Initial area of the spring end 17a ', in particular the

Starting part of the leg, the second single spring 14a '. The stop 29 is at a distance from

Axis of rotational symmetry of the coupling pin 2200. The

The distance of the stop 29 to the axis of rotational symmetry of the coupling pin 2200 can be changed during maintenance, for example with the said adjusting screw VS, which can also be seen in FIG. 12, but - contrary to what the exploded drawing seems to suggest - is not even closer because of this inserted through guide plate 21 to be explained, but screwed below it so that it supports or positions the second end surface 28. By changing the distance, the preload of the second spring changes. In particular, the bias is reduced when the

Distance increased.

As can be clearly seen in FIG. 12, the end region of the spring end 17a ', in particular the beginning part of the leg, of the second individual spring 14a' is cranked, in particular by approximately 90 ° to the start region of the spring end 17a '. In the installed state, the end region of the spring end 17a 'is inserted into an elongated hole 23 arranged in the first centrifugal weight 8a'. As a backup so that the spring end 17a 'is not in operation

accidentally slips out of slot 23 is a

Guide plate 21 provided. The guide plate 21 is on

Eccentric piece 7a attached, in particular screwed. The guide plate 21 has a guide groove 30. The

Guide groove 30 runs approximately parallel to the spring end 17c of the second individual spring 14a 'and approximately orthogonally to the other

Spring end 17a of the second individual spring 14a '.

The elongated hole 23 is optionally (particularly preferred) provided so that the second spring 13 ', in particular the second

Individual spring 14a 'in the operating state below the electrical switching speed, as shown in FIGS. 6, 7 and 11, is not in contact with the centrifugal weight 8b, in the sense that the second spring 13' does not transmit any spring force to the brake and thus in particular not to the spring constant Dl also contributes.

If the speed is increased to electrical switching speed or more, as shown in FIGS. 8, 9 and 10, the second spring 13 ', in particular the second individual spring 14a', bears against the centrifugal weight 8b via the end of the elongated hole 23 in the sense that that the second spring 13 'a spring force on the Brake transmits and thus additionally contributes in particular to the spring constant Dl and a spring constant D2 is created. The electrical switching speed is shown in FIG. 8 and the mechanical switching speed is shown in FIG. 9. It can be seen that both in the state of the electrical and in the

State of the mechanical switching speed

Spring constant D2 is present.

THIRD EMBODIMENT

13 to 16 show the speed limiter 1 '' in a third embodiment. The

Speed limiter 1 ″ in the third exemplary embodiment essentially corresponds to the speed limiter 1 of the first exemplary embodiment, so that the above applies to

Speed limiter 1 after the first

Embodiment also said for the

Speed limiter 1 '' after the third

Embodiment applies except in the second

The essential difference of the speed limiter 1 '' according to the third embodiment compared to

Speed limiter 1 after the first

Embodiment consists in that the second spring of the speed limiter 1 'after the third

Embodiment acts directly between the first flyweight 8a and the second flyweight 8b. The second spring in the third embodiment is by at least one

Coil spring realized, in particular a tension spring with two end hooks. In the following, the principle of operation will be described with reference to the first of the two second individual springs 14a ″, with what has been said correspondingly applicable to the second of the two second individual springs 14b ″. The two flyweights 8a, 8b are each approximately

designed semicircular, a circular recess for receiving the centrifugal weights being provided in the inner region facing the main axis H (FIG. 1). In the area of the circular recess, a bore 31 is provided on the first centrifugal weight 8a. The spring end 17c ″ of the second individual spring 14a ″ is suspended in the bore 31. In the area of the circular recess, an elongated hole 32 is provided on the second centrifugal weight 8b. The spring end 17a ″ of the second individual spring 14a ″ is suspended in the elongated hole 32. Due to the optional elongated hole 32, the spring end 17a '' of the second individual spring 14a '' has regular play up to the electrical switching speed, so that the second spring 13 '', in particular the second individual spring 14a '', does not transmit or transmit any force between the two flyweights 8a, 8b does not exert any force. If the speed is at least the electric

Switching speed increases, the spring end 17a ″ of the second individual spring 14a ″ bears against the end of the elongated hole 32 and the second spring 13 ″, in particular the second individual spring 14a ″, transmits spring forces and thus contributes to increasing the spring constants.

It may be appropriate that the second spring from the

Individual springs 14a '', 14b '' is biased. In particular, the spring is wound with pretension.

The invention comprises a conveying means, not shown in the figures, with a car guided on guide rails, a drive system and a braking device which interacts with the guide rails to terminate a

inadmissible state of motion of the car and a speed limiter 1, 1 ', 1'', as described for the figures. BASIC INFORMATION ON THE FUNCTIONAL PRINCIPLE OF EVERYONE

EMBODIMENTS

Based on Figures 17 to 20, the principle of operation

be explained theoretically.

Fig. 17 shows the general physical behavior of the

Centrifugal force depending on the elevator speed. The centrifugal force is identical to the product of the mass of the

Flyweight multiplied by square

Rotation speed multiplied by the radial distance of the centrifugal weight from the rotation axis:

F _z = m * w ² * r

The resulting centrifugal forces of the centrifugal weight 8a, 8b can vary depending on the design. 17 shows the basic course of the centrifugal force as a function of the elevator speed. The values shown there are for illustration purposes only and must be adjusted depending on the design and local standard requirements.

Up to a defined speed, which is preferably just above the nominal speed, i.e. the usual speed

Operating speed of the elevator increases

Centrifugal force with the square of the (angular) speed omega, as there was no movement of the

Centrifugal weights 8a, 8b takes place to the outside. Will this

If the speed is exceeded, in addition to the increasing speed, the distance r of the center of gravity of the centrifugal weight 8a, 8b to the axis of rotation increases, and the centrifugal force accordingly increases disproportionately because the counterforce caused by the first spring 11 is no longer able to move the centrifugal weight prevent. This leads to the same absolute

Speed increase the centrifugal force in ever greater

increasing scale. In return, the

Counterforce, for example by springs 11, in some

Design characteristics with the movement of the flyweights 8a, 8b only linearly. This leads to higher

Speed range the sensitivity of the

Speed limiter 1 with respect to the

Release speed increases and the setting of the

Speed limiter 1 becomes increasingly difficult in a defined area. This can be seen in particular if the centrifugal force acting on the centrifugal weight 8a, 8b is transferred to the necessary spring force in order to achieve the required centrifugal force

To represent the flyweight movement.

18, the spring force is plotted over the travel path due to the centrifugal force of one of the centrifugal weights 8a, 8b. By preloading the first spring 11, the flyweights 8a, 8b do not move up to at least about the nominal speed (preferably about 2% - 3% above). The spring force uwachs _Z, which is required to move from the electrical switching speed up to the mechanical tripping speed, requires a large part of the travel of the flyweight 8a, 8b. However, since, as can be seen particularly well in FIG. 17, the force, in particular at high angular velocities

increases disproportionately, a clean setting of the means 20 for the detection of electrical and mechanical switching speed is difficult. In addition, the travel path is often limited.

19, the spring force is plotted over the travel path based on the centrifugal force of one of the centrifugal weights 8a, 8b, a non-linear spring or first a first spring 11 and then a second spring 13 connected to the first spring giving the characteristic curve. The second spring 13 is active as soon as the electrical switching speed is reached. From this point, the characteristic curve becomes steeper due to the additional spring force of the second spring 13, which leads to the fact that the necessary flyweight movement between electrical

Switching speed and mechanical switching speed are reduced compared to a system according to FIG. 18.

In addition, with the preload of the first spring 11 and the time at which the second spring 13 comes into effect, the two trigger points (electrical and mechanical

Switching speed) of the speed limiter 1 can be set more easily independently of one another.

20 shows a particularly preferred exemplary embodiment.

20, the second spring 13 is biased, for example against a stop 29. From the electrical

Switching speed, that is, when the second spring 13 transmits a spring force, the bias voltage produces a quasi-sudden increase in the spring characteristic. This can further save the flyweight 8a, 8b

optimized, especially reduced. In addition, the second spring 13 can have a spring characteristic with a flat course, that is to say with a low spring constant D2

exhibit. In particular, the spring constant of the second spring 13 is lower than that of the first spring 11. This means that after the increase in force induced by the preload, a flat characteristic curve can be displayed again, the gradient of which is only slightly greater than the gradient of the characteristic curve of the first spring 11. Thus, again in this area without any special

Sensitivity can be set.

FINAL NOTES OF GENERAL NATURE

Independent protection is also available for one

Speed limiter claimed which has the characteristics of one or more of the following paragraphs, which is optional with features from one or more of the already

drawn up subclaims can be combined and / or with further features from the description.

A speed limiter (1) operated against the forces of a spring system for a hoist, in particular an elevator system, which has a first switching speed, above which it engages a brake, preferably in the form of a brake that brakes the traction sheave or traction sheave shaft, and a second, higher switching speed, when reached he himself

preferably brakes or blocks and then that

Speed limiter cable acted on by train, characterized in that the spring system has a first spring constant (Dl) up to said first switching speed or preferably in any case up to its close range (+/- 20%), that the spring system then has a second one

Spring constant (D2), and that the second

Spring constant (D2) is greater than the first spring constant (Dl).

Speed limiter according to the preceding paragraph, characterized in that the spring system has at least one pair of springs, of which the first spring is the first

Mapping spring constant alone, while the second spring is attached with play so that it does not initially make contact with one in the area of at least one of its ends

Has component against which it can exert a force and the second spring is also fastened in such a way that it comes into contact with the first spring at both ends due to the centrifugal displacement of at least one component of the speed limiter and then the second spring constant together with the first spring maps.

Speed limiter according to the previous two

Heels, characterized in that the spring system has at least one pair of springs, of which one spring is a helical spring and the other spring is a leg or torsion spring, that is to say a spring with a central cylindrical winding, projecting from the legs which twist this winding.

Speed limiter according to one of the three preceding paragraphs, characterized in that the leg or

Torsion spring is penetrated by a holding mandrel.

Speed limiter according to one of the four preceding paragraphs, characterized in that the leg or

Torsion spring is set in its pretension and / or when it takes effect by the fact that the support point of one of the legs is shifted.

REFERENCE SIGN LIST

H major axis

N minor axis

1 speed limiter

2 support structure

3-axis stub

4 rope pulley

5 brake rotors

6 bearing bolts

7a, 7b eccentric pieces

220 coupling pin bore

2200 coupling bolts

8a, 8b centrifugal weights

9 undeflected position

10 reset unit

11 not assigned in the figures (first spring as

Whole)

12a, 12b first individual spring

13 not assigned in the figures (second spring as

Whole)

14a, 14b second individual spring

15a, 15b, 15c, 15d spring end

16 spring-supported

17a, 17b, 17c, 17d spring end

18a, 18b eccentric bolts

19 lock nut

20 means

21 guide plate

22 pen holder

23 slot

24 receiving groove

25 base area

26 opening

27 first end face second end face

attack

Guide groove

drilling

Long hole

Claims

EXPECTATIONS

1. speed limiter (1) for a hoist,

in particular an elevator installation, in turn comprising a rotating one around a main axis (H)

Speed limiter cable driven pulley (4) and a brake for braking the pulley (4), the brake comprising at least one eccentric piece (7a, 7b) pivotally mounted on the pulley (4), the brake having a first flyweight (8a) and a second Centrifugal weight (8b), the eccentric piece (7a, 7b) pivotable on the first centrifugal weight (8a) and pivotable on the second

Centrifugal weight (8b) is mounted, with a

centrifugal displacement of the first and second centrifugal weights (8a, 8b) the first and the second

Centrifugal weight (8a, 8b) pivot the eccentric piece (7a, 7b), the brake being a reset unit (10) with a

Includes spring system that pulls the flyweights (8a, 8b) with the spring force provided by the spring system in the direction of their undeflected position (9)

characterized that the spring system up to one

electrical switching speed of the sheave (4) has a first spring constant (Dl) that the

Spring system from the electrical

Switching speed of the sheave (4) has a second spring constant (D2), and that the second spring constant (D2) is greater than the first spring constant (Dl).

2. Speed limiter according to claim 1,

characterized in that the first spring constant (Dl) is constant.

3. Speed limiter according to claim 1 or 2, characterized in that the second spring constant (D2) is constant.

4. Speed limiter according to one of claims 1 to 3, characterized in that the spring system comprises a first spring (11) with the first spring constant (Dl) and a second spring (13), the second

Spring constant (D2) results from an interaction, in particular from addition, of the spring constants of the first and the second spring (11, 13).

5. Speed limiter according to claim 4,

characterized in that the first spring (11) is a compression spring and is supported on a spring end (15a) on the first flyweight (8a), that the first spring (11) is supported on the other spring end (15c) on a spring support (16) , and that the spring support (16) is operatively connected to the second centrifugal weight (8b).

6. Speed limiter according to claim 4 or 5,

characterized in that the second spring (13 '') is a tension spring, that the second spring (13 '') on one

The spring end (17a '') is attached to the first centrifugal weight (8a), in particular is suspended, and that the second spring (13 '') is attached to the other centreline weight (17c '') on the second centrifugal weight (8b), in particular is suspended.

7. Speed limiter according to one of claims 4 to 6, characterized in that the second spring (13) is a leg spring, that a leg on the

Eccentric piece (7a, 7b) supports, and that the other leg is supported on one of the two flyweights (8a, 8b) at the latest from the electrical switching speed.

8. Speed limiter according to one of claims 4 to 7, characterized in that a stop pin is attached to one of the flyweights (8a, 8b), and that the stop pin serves as a stop for the second spring (13).

9. Speed limiter according to claim 8,

characterized in that the stop pin as

Eccentric bolt (18a, 18b) is executed.

10. Speed limiter according to one of claims 4 to 9, characterized in that the second spring (13)

is biased.

11. Speed limiter according to claim 10,

characterized in that the second spring (13) is adjustably attached to one on the eccentric piece (7a, 7b)

Spring holder (22) is fixed, and that in particular the bias of the second spring (13) is adjustable by adjusting the spring holder (22).

12. Speed limiter according to one of claims 4 to

11,

characterized in that one end of the second spring (13) in an elongated hole (23, 32) to the electrical

Switching speed is movable, and that the slot (23, 32) in particular in one of the two

Flyweights (8a, 8b) is arranged.

13. Speed limiter according to one of claims 4 to 13, characterized in that the brake comprises two eccentric pieces (7a, 7b) pivotably mounted on the rope pulley (4), each of the eccentric pieces (7a, 7b) pivotably on the first centrifugal weight (8a) and swiveling on the second Centrifugal weight (8b) is mounted, with a

Centrifugal weight (8a, 8b) the eccentric pieces (7a, 7b)

pivot that the first spring (11) consists of two first, in particular identical, individual springs (12a, 12b), that each of the first individual springs (12a, 12b) on one of its spring ends (15a, 15b) on one of the two

Support the flyweights (8a, 8b) and each of the first

Support individual springs (12a, 12b) at their other spring ends (15c, 15d) on a spring support (16), the first two individual springs (12a, 12b) being operatively connected to one another via the spring support (16), and in that the second spring (13 ) consists of two second, in particular identical, individual springs (14a, 14b) that in particular from at least the electrical switching speed, each of the second individual springs (14a, 14b) has one spring ends (17a, 17b) on one of the two flyweights (8a , 8b) and at their other spring ends (17c, 17d) each on an eccentric piece (7a, 7b).

14. Speed limiter according to one of claims 1 to 13, characterized in that the first spring (11) is biased and that the first spring (11) is biased so much that the occurring

Centrifugal forces only move the centrifugal weights (8a, 8b) from a speed of at most about 10%, in particular at most about 5%, in particular at most about 2% - 3% above a nominal speed that occurs in normal ferry operation.

15. One against the forces of a spring system

centrifugal force-operated speed limiter (1) for a hoist, in particular an elevator system, which has a first switching speed, when exceeded switches on a brake, preferably in the form of a brake that brakes the traction sheave or traction sheave shaft, and a second, higher switching speed, upon reaching which it preferably brakes or blocks and then applies train speed to the speed limiter cable to trigger at least one further measure, characterized in that that the spring system has a first spring constant (D1) up to said first switching speed or preferably in any case up to its close range (+/- 20%), that the spring system then has a second spring constant (D2), and that the second spring constant ( D2) larger than the first

Spring constant (Dl) is.

16. Speed limiter according to claim 15, characterized

characterized that the spring system at least one

Has pair of springs, of which the first spring the first

The spring constant is shown alone, while the second spring is attached with clearance so that it is in the area

at least one of its ends initially has no contact with a component against which it can exert a force and the second spring is at the same time fastened in such a way that it is displaced by the centrifugal force

at least one component of the speed limiter comes to bear against the first spring at both ends and then together with the first spring the second

Mapped spring constant.

17. Speed limiter according to claim 15 or 16, characterized in that the spring system is at least one

Has pair of springs, one of which is a spring

Coil spring and the other spring is a leg or torsion spring, i.e. a spring with a central one

cylindrical winding, protrude from the legs that twist this winding.

18. Speed limiter according to one of claims 15 to 17, characterized in that the leg or

Torsion spring is penetrated by a holding mandrel.

19. Speed limiter according to one of claims 15 to 19, characterized in that the leg or

Torsion spring is set in its pretension and / or the time when it takes effect by the

Support point of one of the legs is shifted.

20. Funding with a guided on guide rails

Car, a drive system and one with the

Guide rails cooperating braking device for ending an impermissible state of movement of the car and a speed limiter (1) according to one of claims 1 to 19 for triggering the braking and

Safety gear.