ELEVATOR WITH A BRAKE DEVICE

Abstract

An elevator with a brake device may be configured to provide a variable brake force, from a minimum brake force up to a maximum brake force (Vmax). The brake device may include a first energy store that provides the maximum brake force and a second energy store that provides an adjustable counterforce. The adjustable counterforce may be directed in an opposed manner with respect to the maximum brake force provided from the first energy store. Further, the variable brake force may amount to a difference between the maximum brake force and the adjustable counterforce. In some cases, the first energy store may comprise a compression spring for providing the maximum brake force.

Claims

1.-12. (canceled)

13. An elevator comprising a brake device configured to provide a variable brake force from a minimum brake force up to a maximum brake force, the brake device comprising: a first energy store for providing the maximum brake force; a second energy store for providing an adjustable counterforce that is directed in an opposed manner with respect to the maximum brake force, wherein the variable brake force amounts to a difference between the maximum brake force and the adjustable counterforce; a first triggering path and a second triggering path for triggering the brake device, wherein the brake device provides the variable brake force when the first triggering path is active, wherein the brake device provides the maximum brake force when the second triggering path is active; and a triggering element for activating the second energy store when the second triggering path is active, wherein the second energy store is decoupled from the first energy store after activation of the second energy store.

14. The elevator of claim 13 wherein the first energy store comprises a compression spring for providing the maximum brake force.

15. The elevator of claim 13 wherein the second energy store comprises a counter-spring for providing the adjustable counterforce.

16. The elevator of claim 13 further comprising an adjusting element that interacts with the second energy store to set the adjustable counterforce.

17. The elevator of claim 16 wherein the adjusting element comprises an actuator for loading and unloading the second energy store.

18. The elevator of claim 17 wherein the actuator is configured as a hollow shaft drive.

19. The elevator of claim 13 wherein the triggering element comprises a clutch.

20. The elevator of claim 13 wherein the first triggering path is associated with a regulator that sets the variable brake force.

21. The elevator of claim 13 wherein the first triggering path is configured to operate according to an open circuit principle.

22. The elevator of claim 13 wherein the second triggering path is configured to operate according to a closed circuit principle.

23. The elevator of claim 13 wherein the brake device comprises a self-locking gear mechanism for setting the variable brake force, wherein the self-locking gear mechanism is associated with the first triggering path.

24. A brake device for an elevator, the brake device being configured to provide a variable brake force from a minimum brake force up to a maximum brake force, the brake device comprising: a first energy store for providing the maximum brake force; a second energy store for providing an adjustable counterforce that is directed in an opposed manner with respect to the maximum brake force, wherein the variable brake force amounts to a difference between the maximum brake force and the adjustable counterforce; a first triggering path and a second triggering path for triggering the brake device, wherein the brake device provides the variable brake force when the first triggering path is active, wherein the brake device provides the maximum brake force when the second triggering path is active; and a triggering element for activating the second energy store when the second triggering path is active, wherein the second energy store is decoupled from the first energy store after activation of the second energy store.

25. The brake device of claim 24 wherein the first energy store comprises a compression spring for providing the maximum brake force.

26. The brake device of claim 24 wherein the second energy store comprises a counter-spring for providing the adjustable counterforce.

27. The brake device of claim 24 further comprising an adjusting element that interacts with the second energy store to set the adjustable counterforce.

28. The brake device of claim 27 wherein the adjusting element comprises an actuator for loading and unloading the second energy store.

29. The brake device of claim 28 wherein the actuator is configured as a hollow shaft drive.

30. The brake device of claim 24 wherein the triggering element comprises a clutch.

31. The brake device of claim 24 wherein the first triggering path is associated with a regulator that sets the variable brake force.

32. A brake device for an elevator, the brake device being configured to provide a variable brake force from a minimum brake force up to a maximum brake force, the brake device comprising: a first energy store for providing the variable brake force; a second energy store for providing an adjustable counterforce that is directed in an opposed manner with respect to the maximum brake force, wherein the variable brake force amounts to a difference between the maximum brake force and the adjustable counterforce; a first triggering path and a second triggering path for triggering the brake device, wherein the brake device provides the variable brake force when the first triggering path is active, wherein the brake device provides the maximum brake force when the second triggering path is active; and a triggering element for activating the second energy store when the second triggering path is active, wherein the second energy store is decoupled from the first energy store after activation of the second energy store.

Description

DESCRIPTION OF THE FIGURES

[0030] FIG. 1 diagrammatically shows one preferred embodiment of an elevator according to the invention with a brake device, in a diagrammatic illustration.

[0031] FIG. 2 diagrammatically shows one preferred embodiment of a brake device according to the invention.

[0032] FIG. 3 diagrammatically shows further details of the brake device according to FIG. 2.

[0033] FIG. 4 diagrammatically shows further details of the brake device according to FIG. 3.

[0034] FIG. 5 diagrammatically shows a section through one preferred embodiment of the brake device in the open state according to a further embodiment.

[0035] FIG. 6 shows the brake device according to FIG. 5 in the closed state.

[0036] FIG. 7 shows the brake device according to FIG. 5 in the closed state, such that it provides a maximum brake force via a first triggering path.

[0037] FIG. 8 shows the brake device according to FIG. 5 in the closed state, such that it provides a maximum brake force via a second triggering path.

[0038] FIG. 9 diagrammatically shows a section through one preferred embodiment of the brake device in the open state according to a further embodiment.

[0039] FIG. 1 diagrammatically shows one preferred embodiment of an elevator according to the invention which is denoted overall by the designation 2.

[0040] The elevator 2 comprises a car 4 for transporting persons and/or loads, which car 4 can be moved in or counter to the direction of gravity g in an elevator shaft along two guide rails 6a, 6b which run parallel to one another. In a deviation from the present embodiment, however, the car 4 can, for example, also be capable of being moved along a single guide rail.

[0041] A drive 50 which is configured as a traction sheave drive in the present embodiment is provided for moving the car 4. Here, the car 4 can comprise a cabin and a safety frame (both not shown). According to the present embodiment, the drive 50 comprises a suspension means 8, such as suspension ropes, which is fastened to the top side of the car 4. The suspension means 8 runs on a traction sheave 12 which can be driven in a motorized manner by means of a motor (not shown), in order to move the car 4. At the other end which lies opposite the car 4, a counterweight 10 is fastened according to the present embodiment, which counterweight 10 reduces the expenditure of force for moving the car 4 by way of weight equilibrium. In a deviation from the present embodiment, however, another drive can also be used, such as, for example, a linear drive.

[0042] In order to brake the car 4 to a standstill, for example when excess speeds and/or uncontrolled driving movements of the car 4 occur, a brake device 14 is provided which is configured in the present embodiment as a service brake and/or safety catch device and is arranged on both sides of the car 4, with the result that the brake device 14 acts on the two guide rails 6a and 6b.

[0043] FIG. 2 shows the brake device 14 in detail.

[0044] According to the present embodiment, the brake device 14 comprises a regulator 16, an adjusting element 18, a brake unit 20, a comparison unit 22 and an emergency triggering means 24.

[0045] According to the present embodiment, the brake device 14 is released electrically. As an alternative, the brake device can also be released hydraulically or pneumatically.

[0046] In normal operation, a setpoint value SW for the deceleration is fed to the brake device 14 in a manner which is dependent on the degree of loading of the car 4. The setpoint value SW is compared with a measured actual value IW of the deceleration, and the difference, that is to say the regulating deviation, is fed to the regulator 16 which determines an actuating variable ST in a manner which is based on said difference between the setpoint value SW and the actual value IW.

[0047] The actuating variable ST is fed to the adjusting element 18 which transmits a first control signal 51 to the brake unit 20 for providing a variable brake force V between a minimum brake force and a maximum brake force Vmax. The value of the minimum brake force can also be zero. Therefore, a first triggering path I of the brake device 14 is active in normal operation, the first triggering path I comprising the regulator 16 and the adjusting element 18 according to the present embodiment. Therefore, the regulating deviation is fed as an input to the first triggering path I, and the first control signal 51 actuates the brake unit 20 as an output.

[0048] In order to ensure safe operation of the elevator 2 in the case of a failure of the energy supply of the elevator 2 and an associated failure, for example, of the regulator 16 or the adjusting element 18, a second triggering path II is provided.

[0049] In order to activate the second triggering path II, the difference of the setpoint value SW and the actual value IW is compared with a predefined limit value by the comparison unit 22. To this end, the comparison unit 22 can comprise a comparator. If the difference exceeds the predefined limit value, an impermissible excess speed of the car 4 is indicated.

[0050] Upon this, an emergency triggering signal NA is generated by the comparison unit 22 and is transmitted to the emergency triggering means 24. The emergency triggering means generates a second control signal S2 which is transmitted to the brake unit 20 for providing the maximum brake force Vmax. Therefore, a second triggering path II is active in the case of a fault, the second triggering path II comprising the comparison unit 22 and the emergency triggering means 24 according to the present embodiment. Therefore, the difference of the setpoint value SW and the actual value IW is fed as an input to the second triggering path II, and the second control signal S2 actuates the brake unit 20 as an output.

[0051] In order to ensure reliable operation of the brake device 14, for example in the case of an interruption of the energy supply of the elevator 2, the brake device 14 comprises a buffer battery (not shown) which supplies components of the brake device 14, such as, for example, the comparison unit 22, with electric energy.

[0052] Therefore, the brake unit 20 can be actuated in normal operation via the first triggering path I and, in the case of a fault, via the second triggering path II, in order to provide a brake force. Here, the variable brake force V, a regulated brake force according to the present embodiment, is provided via the first triggering path I, whereas the maximum brake force Vmax is provided via the second triggering path II.

[0053] The first triggering path I is therefore not safety-relevant, whereas the second triggering path II is safety-relevant. Therefore, only the components of the second triggering path II are to be designed and checked in a safety-relevant manner.

[0054] In a deviation from the present embodiment, a control of the variable brake force V can also be provided instead of a regulation of the brake force.

[0055] FIG. 3 shows the construction of the adjusting element 18 and the brake unit 20 of the brake device 14 in detail.

[0056] According to the present embodiment, the adjusting element 18 comprises an actuator 26 and a gear mechanism 28 which is connected on the input side to the actuator 26. The actuator 26 can be an electric motor. As an alternative, the actuator can also be a hydraulic or pneumatic cylinder. The gear mechanism 28 can be a self-locking gear mechanism, such as, for example, a spindle mechanism.

[0057] A displacement-force converter 30 of the brake unit 20 is connected on the output side to the gear mechanism 28. Furthermore, according to the present embodiment, the brake unit 20 comprises a clutch 32, a first energy store 34 and a brake 36.

[0058] The displacement-force converter 30 can comprise an elastic element, such as, for example, a spring, which converts a displacement change into a force change. Here, the displacement change is provided by the adjusting element 18 by way of the actuator 26 and the gear mechanism 28. Here, a self-locking configuration of the gear mechanism 28 brings it about that relieving of the elastic element does not take place in the case of deactivation of the adjusting element 18, for example on account of an interruption of the energy supply of the elevator 2, but rather the elastic element maintains its shape.

[0059] In the case of a change from the first triggering path I to the second triggering path II, the clutch 32 decouples the adjusting element 18 from the displacement-force converter 30 and releases brake energy, as will be described later.

[0060] The first energy store 34 provides the maximum brake force Vmax, as will likewise be described later.

[0061] Depending on whether it is triggered via the first triggering path I or the second triggering path II, the brake 36 provides the variable brake force V or the maximum brake force Vmax.

[0062] FIG. 4 shows further details of the displacement-force converter 30, the first energy store 34 and the brake 36 of the brake device 2.

[0063] According to the present embodiment, the displacement-force converter 30 is assigned a second energy store 48. According to the present embodiment, the second energy store is a counter-spring. The first energy store 34 comprises a compression spring 46. Furthermore, FIG. 4 shows that the brake 36 comprises two brake linings 38a, 38b which act on both sides on the guide rail 6a or 6b.

[0064] FIG. 5 diagrammatically shows a section through a first embodiment of the brake device 14 with the brake 36 in the open state.

[0065] It can be seen that the adjusting element 18 with the actuator 26 (shown in FIG. 4) and the gear mechanism 28 is arranged between the displacement-force converter 30 and the first energy store 34.

[0066] Therefore, the first energy store 34 is connected with its first end to the brake lining 38a in a force-transmitting manner, whereas the second end of the brake energy store 34 is connected to the brake housing 44 in a force-transmitting manner. Therefore, the brake device 14 is mounted on the car 4 in a floating manner. A second end of the adjusting element 18 is connected to a first end of the displacement-force converter 30 in a force-transmitting manner.

[0067] Furthermore, it can be seen using FIG. 5 that a second end of the displacement-force converter 30 is connected to a first end of the clutch 32 in a force-transmitting manner. The second end of the clutch 32 is in engagement with a triggering shaft 42 of the brake device 14, which triggering shaft 42 is in turn connected with its front end to the brake lining 38a.

[0068] Furthermore, a stop device 40 is arranged parallel to the displacement-force converter 30, which stop device 40 limits the movement of the clutch 32 in relation to the adjusting element 18, caused by way of stressing or relieving of the displacement-force converter 30.

[0069] The first energy store 34 provides the maximum brake force Vmax, whereas the second energy store 48 provides the adjustable counterforce Vg which reduces the maximum brake force Vmax. The adjustable counterforce Vg can assume values from the minimum brake force up to the maximum brake force Vmax, it also being possible for the minimum brake force to be zero. Therefore, the maximum brake force Vmax and the adjustable counterforce Vg are superimposed in a subtractive manner.

[0070] FIG. 6 shows that, in order to set the variable brake force V, for example according to the comparison of the setpoint value SW and the actual value IW, the adjusting element 18 can be moved along the direction of extent of the triggering shaft 42 by way of the actuator 26 and the gear mechanism 28, after the brake linings 38a, 38b have been brought into contact with the guide rail 6a, 6b. Here, the first triggering path I is active.

[0071] On account of the active clutch 32 which is in engagement with the triggering shaft 42, the adjusting element 18 is moved in the arrow direction A, which brings about relieving of the counter-spring by way of unloading of the second energy store 48. The consequence of this displacement change is that the counter-spring of the second energy store 48 provides a reduced adjustable counterforce Vg, with the result that the variable brake force V which acts is increased. If, in contrast, the adjusting element 18 is moved counter to the arrow direction A, this brings about stressing of the counter-spring by way of loading of the second energy store 48. The consequence of this displacement change is that the counter-spring of the second energy store 48 provides an increased adjustable counterforce Vg, with the result that the variable brake force V which acts is decreased.

[0072] FIG. 7 shows that the movement of the adjusting element 18 in the arrow direction A is limited by the stop device 40. In this situation, the counter-spring of the second energy store 48 does not provide an adjustable counterforce Vg, with the result that the brake device 14 provides the maximum brake force Vmax.

[0073] FIG. 8 shows the brake device 14 in the case of a fault after failure of the energy supply and an associated failure, for example, of the regulator 16 or the adjusting element 18 and the occurrence of an excess speed. Here, the second triggering path II is active.

[0074] The clutch 32 is hereupon deactivated by the triggering element 24, with the result that the clutch 32 is no longer in engagement with the triggering shaft 42. Therefore, the counter-spring of the second energy store 48 is decoupled from the adjusting element 18 by way of releasing. Therefore, no adjustable counterforce Vg which reduces the maximum brake force Vmax of the brake energy store 34 is provided, with the result that the brake device 14 provides the maximum brake force Vmax.

[0075] In order to transfer the brake device 14 into normal operation again after the fault has been eliminated, the adjusting element 18 is activated. As a result, the counter-spring of the second energy store 48 is relieved again. Moreover, the stop device 40 is also driven until the clutch 32 latches on the triggering shaft 42 again at the position which is shown in FIG. 5. Furthermore, the adjusting element 18 is activated, with the result that the adjusting element 18 operates counter to the compression spring 46 of the brake energy store 34, in order thus to release the brake linings 38a, 38b from the guide rail 6a or 6b. The brake device 14 can then be operated in normal operation again.

[0076] FIG. 9 diagrammatically shows a section through the brake device 14 in the open state according to a further embodiment.

[0077] The brake device 14 and its components, namely the adjusting element 18, the first energy store 34 in the form of a compression spring 46, the displacement-force converter 30, the second energy store 48 in the form of a counter-spring, the clutch 32 and the stop device 40 and the brake linings 38a, 38b, are received in a housing 44. Here, the actuator 26 is configured as a hollow shaft drive and is in engagement with the triggering shaft 42. According to this embodiment, the clutch 32 can bring about a transmission of force by way of a frictionally locking connection, which permits particularly rapid activation of the brake 36.