DE202015106367U1 - Electromagnetically releasing spring-loaded brake in the form of a multi-circuit triangular brake - Google Patents

Abstract

Electromagnetically releasing spring pressure brake (BR) for attachment to a machine wall or the like with an axially movable brake rotor (3) with mutually (ie left and right) continuous friction linings (3.1), wherein the spring pressure brake (BR) a coil carrier (1) and a plurality of the coil carrier (1) associated with armature discs (2) and wherein the brake rotor (3) for achieving the braking effect on one (left) side against the machine wall (8) or the like and pressed with the other (right) side against the armature discs (2) is characterized in that the spring pressure brake (BR) has a coil carrier (1) with a triangular base cross-section and that the coil carrier 1, three armature discs 2 are assigned.

Description

In the field of elevator technology, in crane technology and in the field of vertically moving axes, electromagnetically releasing spring-applied brakes have been established for braking and holding the corresponding drives.

Such braking systems must be redundant for safety reasons, which can be achieved by the cultivation of several individual brakes, each with only one brake circuit or by the cultivation of only one brake with multiple internal brake circuits to the drives.

It is common that each of the existing brake circuits makes the same contribution to the total braking torque of the brake. With regard to the redundancy requirements, it is sufficient if, in the event of a brake circuit failure, 100% of the torque required for braking and holding the drive is still provided.

The subject of the invention presented here is an improved spring-applied brake with several internal brake circuits according to the preamble of the main claim.

From the prior art, a spring pressure brake is known, as in DE 10 2005 022 898 A1 is disclosed as a so-called segment brake. In this case, an electromagnetically releasing spring pressure brake for attachment to a machine wall is described which consists of two substantially rectangular shaped coil carriers and two coil carriers associated with the two and substantially rectangular also executed armature discs. The braking effect is achieved in that a rotatably and axially movably connected to a shaft rotor is clamped by the force of springs between the armature discs and a machine wall.

To open the brake, colloquially called airing, the magnetic coils of the bobbin are energized, causing the armature discs are attracted against the force of the springs from the bobbin.

A disadvantage of this spring pressure brake according to the prior art is the small number of brake circuits.

Due to the presence of this brake two brake circuits, the brake reaches a braking torque of 200% of the torque required for braking and holding the drive during normal operation. In case of failure of a brake circuit thus 100% of the required braking torque are available. The design of all machine components must take into account the maximum braking torque of 200%, which in some cases results in heavier and more complex designs.

In the case of an emergency stop, therefore, for example, the passengers of an elevator are exposed to very high acceleration forces. In addition, the brake requires according to the prior art presented because of the two existing coil support a relatively high handling and assembly costs: It must be mounted and adjusted two coil carriers, each with a plurality of fasteners to the machine wall.

A development of the above-discussed spring pressure brake is from the DE 10 2006 016 434 A1 known. This brake also has two brake circuits, but the coil carrier designed substantially with a rectangular cross-section is made in one piece and also equipped with two rectangular armature discs.

By the construction disclosed in this document, the cost of handling and assembly of the brake can be significantly reduced, d. H. it is only the cultivation and adjustment of a bobbin required. However, this brake has only two brake circuits, so that here in normal operation with proper function of both brake circuits 200% of the required for braking and holding the drive torque are available. All components of the corresponding system must therefore be designed for this increase in braking torque to 200% - with all known disadvantages.

Furthermore, from the EP 2 201 260 B1 another spring pressure brake in the form of a so-called four-segment brake known. In this case, a brake is disclosed which has a preferably square coil carrier with four individual coils arranged therein, wherein each individual coil is assigned a square armature disk. As a result, the brake can be designed so that 133% of the torque required to brake and hold the drive are available with perfect operation of all four brake circuits and that the brake thus provides 100% of the braking torque in case of failure of a brake circuit.

This makes it possible on the one hand to build the brake as such smaller, and on the other hand, the other components of the system can be designed for lower braking loads and thus be realized easier and cheaper.

A disadvantage of the so-called four-segment brake, the high number of partially complicated to manufacture components and the so accompanying increased effort for handling and installation of the brake. Since in multi-circuit brakes and the function of each brake circuit must be monitored individually by sensing the stroke of the armature discs via microswitch, four micro-switches are installed in the four-segment brake, adjust and connect to the control of the customer, which is a considerable effort on the part of Manufacturer and the user of the brake means.

• – Einfacher kompakter Aufbau der Bremse mit wenigen Funktionsteilen.
• – Kostengünstige Herstellung der Bremse und deren Komponenten.
• – Robuste Ausführung der Bremse.
• – Ausreichende Zahl von Bremskreisen für geringe Überhöhung des maximalen Bremsmoments.
• – Einfaches Handling und einfacher Einbau der Bremse beim Kunden.

The object of the present invention is therefore to specify a multi-circuit electromagnetically releasing spring pressure brake which fulfills the following additional requirement profile compared with the spring pressure brakes according to the known state of the art:

• - Simple compact design of the brake with few functional parts.
• - Cost-effective production of the brake and its components.
• - Robust design of the brake.
• - Sufficient number of brake circuits for slight increase in the maximum braking torque.
• - Easy handling and easy installation of the brake at the customer.

This task profile is achieved by an electromagnetically releasing spring-loaded brake with the features of claim 1.

Accordingly, it is proposed to design the spring-pressure brake such that the coil carrier has essentially the shape of a triangle. Furthermore, it is proposed that the magnetic coils are preferably designed to be round and are arranged in the region of the corners of the triangle. Finally, it is proposed that each magnet coil is associated with an armature disk in a preferably round shape.

This results in an electromagnetically releasing spring pressure brake with three brake circuits, which in terms of design of the braking torque in normal operation and failure of a brake circuit with a ratio of 150% to 100% has only a relatively small increase in the braking torque.

In terms of the technical effort for production, handling and cultivation, the brake still results in significant advantages compared to the known state of the art.

Due to the triangular shape of the bobbin, the brake can be built significantly more compact, lighter and resource-saving than the presented systems according to the prior art.

Above all, by the possible attachment of the bobbin to a machine wall in a statically determined manner by attachment over three points located in the region of the corners of the bobbin points handling and installation of the brake are much easier.

Due to the presence of three brake circuits, only the movements of three armature discs have to be monitored and evaluated, for which only three sensors have to be mounted, adjusted and connected to the control of the user

Furthermore, it is possible to adapt the outer contours of the coil carrier and the three armature discs so that the armature discs are designed as simple turned parts. Accordingly, the three magnetic coils can be geometrically simply provided in a round, preferably circular design.

It can be summarized that a brake is presented by the construction of the spring pressure brake according to the invention briefly described here, which has a small torque increase with significant advantages over the prior art in terms of production, handling and cultivation.

Other features and advantageous details of the spring pressure brake according to the invention will become apparent from the description of the preferred embodiments shown below.

Show it:

1 the perspective view of a drive motor with an attached spring pressure brake

2 an exploded perspective view of the drive motor with the spring pressure brake according to the invention

3 a front view of the drive 1

4 a longitudinal section AA through the drive with brake 3

5 a longitudinal section BB through the drive with brake 3

6 a detailed view B from the longitudinal section BB of 5

7 a view C from 3

8th a detailed view D from the view C of 7 ,

Out 1 is the basic structure of the spring pressure brake invention (BR) and their attachment to the end wall ( 6 ) of a motor (M) can be seen. Accordingly, the spring-pressure brake (BR) is concentric with the axis of rotation (R) of the motor (M) on the machine wall ( 6 ), wherein the coil carrier ( 1 ) of the brake (BR) via spacers ( 4 ) and screws ( 5 ) is firmly connected to the motor (M).

The coil carrier ( 1 ) are three armature discs ( 2 ) assigned relative to the bobbin ( 1 ) are axially movable but rotatably mounted. Between the anchor discs ( 2 ) and the counter friction surface ( 6 ) is a brake rotor ( 3 ), which on the the coil carrier ( 1 ) and the machine wall ( 6 ) facing flat surfaces with annular friction linings ( 3.1 ) is equipped. On the side of the coil carrier facing away from the motor (M) there are three manual release levers ( 7 ), with the three armature discs ( 2 ) of the spring pressure brake (BR) are in operative connection.

Further details of the spring pressure brake (BR) according to the invention are shown in the exploded view in FIG 2 seen. The spring pressure brake (BR) is shown in a state in which it is removed from the engine (M) and in which the brake rotor ( 3 ) from the motor shaft ( 8th ) is deducted.

The illustrated spring pressure brake (BR) consists of a coil carrier ( 1 ) and three armature discs ( 2 ), which are designed in an advantageous manner as a largely circular discs. The armature discs are on the in holes of the bobbin ( 1 ) pressed guide pin ( 9 ) rotatably and axially movable on the bobbin ( 1 ) guided. On the front of the spring-loaded brake (BR) are again the three hand release levers ( 7 ) shown with nuts ( 7.2 ) provided tie rods ( 7.1 ) with the anchor discs ( 2 ) interact.

The brake rotor ( 3 ) is on both sides with friction linings ( 3.1 ) and is above the rotor toothing ( 3.2 ) with the shaft toothing ( 8.1 ) of the motor shaft ( 8th ), whereby the brake rotor ( 3 ) rotatably and axially displaceable on the motor shaft ( 8th ) is stored.

3 shows a front view of the engine (M) from which the concentric mounting of the spring pressure brake (BR) on the machine wall ( 6 ) as well as the arrangement of the three hand release levers ( 7 ) on the bobbin carrier ( 1 ) are clearly visible.

In 4 is a first longitudinal section AA through the spring pressure brake (BR) 3 shown. This is the cultivation of the coil carrier ( 1 ) of the spring-pressure brake (BR) on the machine wall ( 6 ) via spacers ( 4 ) and screws ( 5 ) can be seen. Furthermore, in the axial bores of the bobbin ( 1 ) located compression springs ( 10 ) as well as in axial incisions of the bobbin carrier ( 1 ) inserted magnetic coils ( 1.1 to see). Via guide pins ( 9 ) are the three anchor discs ( 2 ) rotatably and axially movable with the coil carrier ( 1 ) connected. Between the anchor discs ( 2 ) and the machine wall ( 6 ) is located on both sides with friction linings ( 3.1 ) and on the shaft toothing ( 8.1 ) rotatably and axially movably mounted brake rotor ( 3 ).

In the braked state of the engine (M), the force of the compression springs ( 10 ) on the armature discs ( 2 ) and thus biases the brake rotor ( 3 ) between the armature discs ( 2 ) and the machine wall ( 6 ) one. Through the magnetic coils ( 1.1 ) in the coil carrier ( 1 ) no electricity flows. To open the spring-loaded brake (BR) to the coil carrier ( 1 ) embedded magnetic coils ( 1.1 ) applied an electrical voltage, whereby a magnetic field is built, the armature discs ( 2 ) against the force of the compression springs ( 10 ). The motor shaft ( 8th ) with the brake rotor ( 3 ) is thus freely rotatable.

• – Zu erwähnen ist zunächst die Handlüftvorrichtung, deren Aufgabe es ist, durch eine manuelle Aktion die Ankerscheiben (2) gegen die Kraft der Druckfedern (10) zu bewegen und damit eine freie Drehung des Bremsrotors (3) und der damit verbundenen Motorwelle (8) zu ermöglichen. Diese Funktion wird hauptsächlich bei Stromausfall genutzt. Die Handlüftvorrichtung besteht dabei aus einem als Schraube gebildeten Zuganker (7.1), der den Handlüfthebel (7), den Spulenträger (1), jeweils eine Ankerscheibe (2) und den Stützring (7.5) durchdringt und auf der Rückseite des Handlüfthebels (7) mit einer Mutter (7.2) gesichert ist. Zwischen dem Handlüfthebel (7) und dem Spulenträger (1) sind in Senkungen (7.6) Wälzkörper (7.4) in Form von Kugeln eingelegt, die im Normalbetrieb der Federdruckbremse (BR) durch eine Haltefeder (7.3) im Eingriff gehalten werden. Bei Verdrehung des Handlüfthebels (7) um die Längsachse des Zugankers (7.1) gleiten die Wälzkörper (7.4) aus den Senkungen (7.6) des Handlüfthebels (7) heraus. Dadurch vollführen der Handlüfthebel (7) und die Mutter (7.2) mit dem Zuganker (7.1) eine Axialbewegung gegen die Kraft der Haltefeder (7.3) und bewirken letztlich über den Stützring (7.5) eine Bewegung der Ankerscheibe (2) gegen die Kraft der Druckfedern (10), bis der Bremsrotor (3) entlastet wird und sich mit der Motorwelle (8) frei drehen lässt.
• – Weiterhin ist die beschriebene Federdruckbremse (BR) mit einer Einrichtung zur Geräuschdämpfung ausgestattet, deren räumliche Lage aus Detail B in 5 hervorgeht.

5 shows a further longitudinal section BB through the spring pressure brake (BR) according to the invention 3 , This shows two more technical features of the brake:

• - To mention is first the manual release device, whose task is, by a manual action, the armature discs ( 2 ) against the force of the compression springs ( 10 ) and thus a free rotation of the brake rotor ( 3 ) and the associated motor shaft ( 8th ). This feature is mainly used in case of power failure. The manual release device consists of a tie rod formed as a screw ( 7.1 ), the hand release lever ( 7 ), the coil carrier ( 1 ), one anchor plate each ( 2 ) and the support ring ( 7.5 ) and on the back of the hand release lever ( 7 ) with a mother ( 7.2 ) is secured. Between the manual release lever ( 7 ) and the coil carrier ( 1 ) are in subsidence ( 7.6 ) Rolling elements ( 7.4 ) in the form of balls, which in normal operation of the spring-loaded brake (BR) by a retaining spring ( 7.3 ) are kept in engagement. When rotating the hand release lever ( 7 ) about the longitudinal axis of the tie rod ( 7.1 ) the rolling elements ( 7.4 ) from the subsidence ( 7.6 ) of the hand release lever ( 7 ) out. As a result, the hand release lever ( 7 ) and the mother ( 7.2 ) with the tie rod ( 7.1 ) an axial movement against the force of the retaining spring ( 7.3 ) and ultimately bring about the support ring ( 7.5 ) a movement of the armature disk ( 2 ) against the force of the compression springs ( 10 ), until the Brake rotor ( 3 ) and with the motor shaft ( 8th ) can rotate freely.
• - Furthermore, the described spring pressure brake (BR) is equipped with a device for noise damping, the spatial position of detail B in 5 evident.

In 6 this detail B is shown enlarged. Accordingly, the device for noise damping ( 11 ) from an axial into the coil carrier ( 1 ) screwed in threaded pin ( 11.1 ) and a counter nut assigned thereto ( 11.2 ), whereby the grub screw ( 11.1 ) with his the anchor plate ( 2 ) associated end via a pressure plate ( 11.3 ) an elastomeric ring ( 11.4 ) and a concentric damping plate ( 11.5 ).

The two concentric damping elements, ie the elastomer ring ( 11.4 ) and the damping plate ( 11.5 ) can be replaced by the grub screw ( 11.1 ) are adjusted in the axial direction so that they permanently or only when opening the spring pressure brake (BR) in contact with the armature disc ( 2 ) stand. By adjusting the axial position of the damping elements via the threaded pins ( 11.1 ) and by matching the thickness and / or hardness of the damping elements, the spring pressure brake (BR) with respect to the noise during opening and / or closing can be optimally damped.

Out 7 in the shape of the view C is ultimately the spatial position of a in a recess of the bobbin ( 1 ) arranged sensor ( 12 ), the object of which is to determine the axial position of the armature disk ( 2 ) to the coil carrier ( 1 ) and thus to detect the open or closed state of the spring-applied brake (BR) and to report to a monitoring device, not shown.

The sensor ( 12 ) can as shown as a mechanical switch with a switch plunger ( 12.1 ), which is connected via an armature disk ( 2 ) connected adjusting screw ( 12.2 ) with lock nut ( 12.3 ) the axial movement of the armature disc ( 2 ) detected.

Likewise, the sensor may be designed as a non-contact proximity switch whose adjustment by adjusting the illustrated adjusting screw ( 12.2 ) or by an axial displacement of the position of the sensor ( 12 ) to the anchor plate ( 2 ).

LIST OF REFERENCE NUMBERS

1

coil carrier

1.1

solenoid

2

armature disc

3

brake rotor

3.1

friction lining

3.2

rotor teeth

4

Distanzbuchse

5

screw

6

machine wall

7

manual release lever

7.1

tie rods

7.2

mother

7.3

retaining spring

7.4

rolling elements

7.5

support ring

7.6

reduction

8th

motor shaft

8.1

shaft splines

9

guide pins

10

compression spring

11

Device for noise damping

11.1

Set screw

11.2

locknut

11.3

thrust washer

11.4

elastomer ring

11.5

damping plate

12

sensor

12.1

switching plunger

12.2

adjustment

12.3

locknut

BR

Spring-loaded brake

M

engine

R

axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102005022898 A1 [0005]
• DE 102006016434 A1 [0010]
• EP 2201260 B1 [0012]

Claims (12)

Electromagnetically releasing spring pressure brake (BR) for mounting on a machine wall or similar with an axially movable brake rotor (BR) 3 ) with mutually (ie left and right) continuous friction linings ( 3.1 ), wherein the spring-pressure brake (BR) a coil carrier ( 1 ) and several the coil carrier ( 1 ) associated armature discs ( 2 ) and wherein the brake rotor ( 3 ) to achieve the braking effect on the one (left) side against the machine wall ( 8th ) or the like and with the other (right) side against the armature discs ( 2 ) is pressed, characterized in that the spring pressure brake (BR) a coil carrier ( 1 ) having a triangular basic cross-section and that the coil carrier 1 three anchor discs 2 assigned. Spring-loaded brake (BR) according to claim 1, characterized in that in the coil carrier ( 1 ) three annular magnetic coils ( 1.1 ) are arranged. Spring-loaded brake (BR) according to claim 1, characterized in that in the coil carrier ( 1 ) three groups of annular magnetic coils ( 1.1 ), wherein these groups each consist of at least two individual coils. Spring-loaded brake (BR) according to at least one of the preceding claims, characterized in that the armature discs ( 2 ) have a round basic geometry. Spring-loaded brake (BR) according to at least one of the preceding claims, characterized in that the armature discs ( 2 ) for opening the spring pressure brake individually by manually operated manual release lever ( 7 ) against the force of the compression springs ( 10 ) are movable. Spring pressure brake BR according to at least one of the preceding claims, characterized in that the lifting movement of each armature disc 2 through a sensor 12 is detected. Spring pressure brake (BR) according to at least one of the preceding claims, characterized in that the lifting movements of the armature discs ( 2 ) are detected by mechanical switches. Spring pressure brake (BR) according to at least one of the preceding claims, characterized in that the lifting movements of the armature discs ( 2 ) are detected by non-contact switch. Spring-loaded brake (BR) according to at least one of the preceding claims, characterized in that the impact noise of the armature discs ( 2 ) on the bobbin carrier ( 1 ) and / or the brake rotor ( 3 ) are muffled. Spring pressure brake (BR) according to at least one of the preceding claims, characterized in that for damping the impact noise of the armature discs ( 2 ) Elastomer rings ( 11.4 ) and / or damping plates ( 11.5 ) be used. Spring pressure brake (BR) according to at least one of the preceding claims, characterized in that the axial prestress of the elastomeric rings ( 11.4 ) and / or damping plates ( 11.5 ) is designed adjustable. Spring pressure brake (BR) according to at least one of the preceding claims, characterized in that the braking torque of the spring pressure brake (BR) by varying the axial bias of the compression springs ( 10 ) and / or by varying the number of compression springs ( 10 ) is adjustable.

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